A multi-dimensional and multi-mode pipeline vibration isolation device

Abstract

The present invention discloses a multi-dimensional and multi-mode pipeline vibration isolation device, which belongs to the field of pipeline vibration isolation technology and solves the technical problems in the prior art regarding the multi-dimensional vibration and weak vibration isolation effect of pipelines. It includes a plurality of vibration isolation units for supporting pipelines, and the plurality of vibration isolation units include a support seat body and a plurality of vibration isolation layers arranged on the support seat body; the support seat body includes a support portion one, a support portion two, and a connecting portion; the plurality of vibration isolation layers include a support layer covering the support portion one, a constraint layer and a damping layer covering the support portion two in turn; the support portion two is provided with a through hole, a support rod is transversely arranged in the through hole, and a mass block is sleeved on the middle section of the support rod. The multi-dimensional and multi-mode pipeline vibration isolation device of the present invention can be better used for multi-dimensional vibration isolation of pipelines, has a wide range of applications, a simple structure, and is easy to use.

Description

Technical Field

[0001] The present invention relates to the technical field of pipeline vibration isolation, and in particular to a multi-dimensional and multi-mode pipeline vibration isolation device. Background Art

[0002] Pipelines are an effective means of transporting natural gas, oil, and other energy sources over long distances, with relatively low transportation cycles and costs. While pipeline transportation offers advantages in cost and operational efficiency, the vibrations associated with pipeline transportation can harm pipeline systems, regulating valves, and other components, causing failure and damage. This, in turn, impacts the effective operation of the pipeline system and reduces the pipeline's transportation advantages. Pipeline vibration reduction has become a key issue in pipeline operation and maintenance. Pipeline vibration originates from two sources: first, vibrations generated by large compression equipment during operation, which are transmitted to the pipeline and propagate in multiple directions. Second, changes in fluid pressure within the pipeline create flow pressure pulsations, which stimulate vibrations in the pipeline system that propagate in multiple directions. Because pipeline vibration sources are diverse and generate multiple dimensions of pipeline response, effectively isolating multi-mode and multi-dimensional pipeline vibrations is a pressing issue in transportation production.

[0003] Currently, pipeline vibration isolation and reduction primarily include active, semi-active, and passive methods. Passive vibration isolation offers excellent stability, requires no external energy supply, is economical and durable, and is widely used in pipeline transportation. However, currently widely used passive vibration isolation primarily targets vibration perpendicular to the pipeline wall. There are relatively few isolators capable of multi-directional vibration isolation, and they lack the ability to dissipate energy transmitted through the pipeline, resulting in poor pipeline vibration isolation effectiveness. Summary of the Invention

[0004] The purpose of the present invention is to provide a multi-dimensional and multi-mode pipeline vibration isolation device to solve the technical problem of poor pipeline vibration isolation effect in the prior art.

[0005] To achieve the above objectives, the present invention provides the following technical solutions:

[0006] The present invention provides a multi-dimensional and multi-mode pipeline vibration isolation device, comprising a plurality of vibration isolation units for supporting pipelines, wherein the vibration isolation units comprise a support seat body and a plurality of vibration isolation layers arranged on the support seat body; the support seat body comprises a support portion one, a support portion two and a connecting portion; the support portion two is a two-section type and is symmetrically arranged about the support portion one, and the two sections of the support portion two are respectively connected to the connecting portion; the plurality of vibration isolation layers comprise a support layer covering the support portion one, a constraint layer and a damping layer covering the support portion two in sequence; a through hole is provided on the support portion two, a support rod is transversely arranged in the through hole, both ends of the support rod are engaged and connected with the support portion two, and a mass block is sleeved on the middle section of the support rod.

[0007] Optionally or preferably, the support part one, the support part two and the connecting part are integrally connected, and the cross-section of the support part one, multiple support parts two and multiple connecting parts after being integrally connected is a trapezoidal structure, the support part one is arranged along the plane where the top edge of the trapezoid is located, the support part two is arranged along the plane where the two waist edges of the trapezoid are located, and the connecting part is integrally connected to the bottom end of the support part two; the connecting part is provided with multiple bolts for fixing to the ground.

[0008] Optionally or preferably, the support part 1 and the support layer are bent downward, and the curvature is the same as the curvature of the outer diameter of the pipe; the support part 2 and the constraint layer and damping layer covering the support part 2 are all bent toward the center of the support seat body.

[0009] The technical effect of adopting the above technical solution is: through the trapezoidal structure and multiple curved structures of the support seat body, it can be better used to isolate the external radial excitations on the pipeline and to isolate the axial vibration of the pipeline, and at the same time can also attenuate the vibration in the corresponding direction caused by the change of the flow velocity of the fluid in the pipeline.

[0010] Optionally or preferably, the support seat body, damping layer and support rod are all made of viscoelastic damping materials; the mass block is a metal block; the thickness of the support layer, constraint layer and damping layer is 1.5-5mm; the support layer and constraint layer are metal plates.

[0011] Optionally or preferably, the plurality of vibration isolation units are closely connected or spaced apart from each other.

[0012] The technical effect of adopting the above technical solution is: different arrangements of the vibration isolation units can bring different vibration isolation effects in actual pipeline vibration isolation work; specifically, different arrangements are selected according to different pipeline vibration frequencies.

[0013] A design method for a multi-dimensional and multi-mode pipeline vibration isolation device includes the following steps:

[0014] S1. Determine the design frequency f of ground vibration excitation on the pipeline in all directions x 、f y 、f z The y-axis is the direction along the axial direction of the pipeline, the x-axis is the direction along the horizontal radial direction of the pipeline, and the z-axis is the direction perpendicular to the horizontal radial direction of the pipeline.

[0015] S2. Determine different vibration isolation modes of the support base body caused by the vibration of the pipeline in various directions; the vibration isolation modes are deformation modes of the support base body;

[0016] When the pipeline excites the support base body in the x-axis direction, the vibration isolation form of the support base body is shear and bending deformation;

[0017] When the pipeline excites the support base body in the y-axis direction, the vibration isolation form of the support base body is bending deformation;

[0018] When the pipeline excites the support base body in the z-axis direction, the vibration isolation form of the support base body is shear deformation;

[0019] S3. Determine the stiffness K of the pipeline in each direction x , K y , K z Then the circular frequency ω of the support body in each direction is obtained x 、ω y 、ω z ;

[0020] S4, by design frequency f x 、f y 、f z , the circular frequency of the support body in each direction ω x 、ω y 、ω z And the stiffness K of the pipe in all directions x , K y , K z Obtaining the geometric parameters of the support seat body;

[0021] S5. Determine the mass of the mass block.

[0022] Optionally or preferably, the stiffness K in each direction of the pipe in S3 x , K y , K z Get the circular frequency ω of the support body in each direction x 、ω y 、ω z The method comprises the following steps:

[0023] S31. Calculate the stiffness K of the pipeline in each direction x , K y , K z :

[0024] Pipe stiffness K in the x-axis direction x for:

[0025] K x =(2~6)K z

[0026] Pipe stiffness K in the y-axis direction y for:

[0027] K y =2A L m y G / H

[0028] in,

[0029] A L =L·B

[0030] m y =1 / (1+0.29(H / L) 2 )

[0031] Where G is the shear elastic modulus of the material selected for the support base body, H is the vertical height of the cross section of the support part 2, m y is the calculation coefficient, B is the cross-sectional width of the support part 2, L is the front width of the support part 2, A L is the horizontal cross-sectional area of the support portion 2;

[0032] Pipe stiffness K in the z-axis direction z for:

[0033] K z =4πHG / ln(R H / R B )

[0034] Among them, m is the mass of the support body, R H R is the distance from the connection between support part 2 and support part 3 to the center line of the cross section of the support base body; B is the projection width of the second support part on the ground;

[0035] S32. Obtain the stiffness K of the pipeline in each direction x , K y , K z and the circular frequency ω of the support body in all directions x 、ω y 、ω z :

[0036] Circular frequency ω of the pipeline in the x-axis direction x for:

[0037]

[0038] Circular frequency ω of the pipeline in the y-axis direction y for:

[0039]

[0040] Circular frequency ω of the pipeline in the z-axis direction z for:

[0041]

[0042] As an optional implementation, in S4, the frequency f is designed x 、f y、f z , the circular frequency of the support body in each direction ω x 、ω y 、ω z And the stiffness K of the pipe in all directions x , K y , K z The method for obtaining the geometric parameters of the support seat body comprises the following steps:

[0043] S41, according to the design frequency f x 、f y 、f z , the circular frequency ω of the pipeline in the x-axis, y-axis, and z-axis directions x 、ω y 、ω z Pipe stiffness K in all directions x , K y , K z Get the stiffness K x , K y , K z With the design frequency f x 、f y 、f z The relationship:

[0044] K n =4π 2 mf n 2

[0045] Where n = x, y, z;

[0046] S42, combined with the stiffness K of the pipe in the z-axis direction in S31 z The geometric parameters H and R of the support body can be obtained H 、R B Relationship with design frequency fz:

[0047] H / ln(R H / R B )=πmf z 2

[0048] S43, combined with the stiffness K of the pipe in the y-axis direction in S31 y The geometric parameters B, L, H and design frequency f of the support body can be obtained y Relationship:

[0049] BL 3 / (HL 2 +0.29H 3 )=2π 2 mf y2 / G

[0050] Optionally or preferably, the method for determining the mass of the mass block in S5 comprises the following steps:

[0051] S51. Determine the relationship between the support rod resonance frequency f and the mass of the mass block:

[0052] The two ends of the support rod are fixed to the support part 2 through the through holes. The motion equation of the support rod is:

[0053]

[0054] After separating the variables:

[0055] d 4 y(x) / d 4 xk 4 y(x)=0

[0056] Where A is the cross-sectional area of the support rod, l is the length of the support rod, ρ is the density of the support rod, and EI is the bending stiffness of the support rod. Both k and a are calculation coefficients:

[0057] k 4 =ω 2 / a 2

[0058] a 2 =EI / (ρA)

[0059] After calculation, the relationship between the resonant frequency f of the support rod and the support rod density ρ is obtained:

[0060]

[0061] S52. Since the mass block is connected to the support rod, the mass of the mass block is adjusted to adjust the mass of the support rod, thereby adjusting the resonance frequency of the support rod and the resonance frequency of the entire device.

[0062] Based on the above technical solution, the embodiments of the present invention can produce at least the following technical effects:

[0063] The multi-dimensional and multi-mode pipeline vibration isolation device provided by the present invention has multiple vibration isolation units that cooperate with each other. Vibrations in different directions generated outside the pipeline can be effectively suppressed through the support base body on each vibration isolation unit and the multiple vibration isolation layers arranged on the support base body. Through different setting methods of the vibration isolation units and methods of adjusting the mass of the mass block, the excitation of the pipeline in all directions is better suppressed, and adaptive adjustment can be made according to actual working conditions. In addition, vibrations caused by changes in flow velocity in the pipeline can also be transmitted and attenuated through the device. For multi-peak or broadband vibration modes, multiple vibration isolation devices can also be combined in series or the arrangement of the devices can be changed to control the transmission of vibration energy. BRIEF DESCRIPTION OF THE DRAWINGS

[0064] Figure 1 It is a schematic diagram of the overall structure of the vibration isolation unit in the multi-dimensional and multi-mode pipeline vibration isolation device of the present invention;

[0065] Figure 2 is a cross-sectional view of a vibration isolation unit in the multi-dimensional and multi-mode pipeline vibration isolation device of the present invention;

[0066] Figure 3 yes Figure 2 A partial enlarged view of part A in the middle;

[0067] Figure 4 This is the geometric parameter indication of the support body in the multi-dimensional multi-mode pipeline vibration isolation device of the present invention. Figure 1 ;

[0068] Figure 5 This is the geometric parameter indication of the support body in the multi-dimensional multi-mode pipeline vibration isolation device of the present invention. Figure 2 ;

[0069] Figure 6 This is a diagram showing the actual effect of the cooperation between the vibration isolation unit and the pipeline in the multi-dimensional and multi-mode pipeline vibration isolation device of the present invention;

[0070] Figure 7 The vibration isolation unit in the multi-dimensional multi-mode pipeline vibration isolation device of the present invention is connected to the pipeline Figure 1 ;

[0071] Figure 8 The vibration isolation unit in the multi-dimensional multi-mode pipeline vibration isolation device of the present invention is connected to the pipeline Figure 2 ;

[0072] Figure 9 1 is a frequency-vibration transmission loss diagram of different configurations of the vibration isolation units of Example 1 and Example 2 of the present invention.

[0073] In the figure: 1. Support seat body; 11. Support part 1; 12. Support part 2; 13. Connecting part; 2. Mass block; 3. Support layer; 4. Constraint layer; 5. Damping layer; 6. Pipe; 7. Through hole; 8. Support rod. DETAILED DESCRIPTION

[0074] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work shall fall within the scope of protection of the present invention.

[0075] [Example 1]

[0076] See also Figures 1 to 3 A multi-dimensional and multi-mode pipeline vibration isolation device includes multiple vibration isolation units for supporting pipelines 6, and the multiple vibration isolation units include a support seat body 1 and multiple vibration isolation layers arranged on the support seat body 1; the support seat body 1 includes a support part 11, a support part 2 12 and a connecting part 13; the support part 2 12 is a two-section type and is symmetrically arranged about the support part 11, and the two sections of the support part 2 12 are respectively connected to the connecting part 13; the support seat body 1 is fastened to the ground by bolting or welding with the ground through the connecting part 13, and the pipeline 6 is connected to the support part 11 by bolts or welding.

[0077] The multiple vibration isolation layers include a support layer 3 covering the support part 11, a constraint layer 4 and a damping layer 5 sequentially covering the support part 2 12; in this embodiment, the support layer 3 is firmly bonded to the support part 11 by high-pressure vulcanization.

[0078] The second support portion 12 is provided with a through hole 7 , a support rod 8 is transversely provided in the through hole 7 , both ends of the support rod 8 are engaged with the second support portion 12 , and a mass block 2 is sleeved on the middle section of the support rod 8 .

[0079] As an optional embodiment, the support portion 11, the support portion 2 12 and the connecting portion 13 are integrally connected, and the cross-section of the support portion 11, the plurality of support portions 2 12 and the plurality of connecting portions 13 after being integrally connected is a trapezoidal structure, the support portion 11 is arranged along the plane where the top side of the trapezoid is located, the support portion 2 12 is arranged along the plane where the two waist sides of the trapezoid are located, and the connecting portion 13 is integrally connected to the bottom end of the support portion 2 12;

[0080] As an optional embodiment, the support part 11 and the support layer 3 are bent downward, and the bending curvature is the same as the curvature of the outer diameter of the pipe 6; the support part 2 12 and the constraint layer 4 and the damping layer 5 covering the support part 2 12 are all bent toward the center of the support seat body 1.

[0081] As an optional embodiment, the support seat body 1, the constraint layer 4 and the support rod 8 are all viscoelastic damping materials; the mass block 2 is a metal block; the thickness of the support layer 3, the constraint layer 4 and the damping layer 5 is 1.5mm-5mm; the support layer 2 and the damping layer 5 are metal plates.

[0082] In this embodiment, the support seat body 1, the support rod 8 and the damping layer 5 are made of viscoelastic materials such as lead core, asphalt damping, numerical damping, etc.

[0083] See also Figure 7 Multiple vibration isolation units are arranged at intervals from each other, respectively connecting the pipeline 6 and the ground, and the interval between adjacent vibration isolation units is 76 mm.

[0084] [Example 2]

[0085] See also Figure 8 Based on the first embodiment, this embodiment connects multiple vibration isolation units tightly and then arranges them in sections to achieve different vibration isolation effects.

[0086] In Example 1 and Example 2, the vibration isolation unit is set in different ways. A circular boundary is selected in the middle of the pipe 6 as the excitation point, and a response measurement point is selected at the end of the pipe side wall. The frequency-vibration transmission loss diagrams of the two vibration isolation unit settings are as follows: Figure 9 As shown in the figure, the results show that spacing the isolation units apart can effectively attenuate vibration frequencies below 2000Hz, especially at 800Hz-1000Hz, which is the resonant frequency of the mass oscillator. It can absorb the vibration energy propagating on the pipeline through the resonance effect and dissipate the energy through rubber damping. The periodic arrangement method in which multiple isolation units are tightly connected and then arranged in sections has a stronger ability to attenuate energy propagation than the interval arrangement method. Therefore, through different periodic arrangements, the isolation units can have better vibration energy propagation loss capabilities. By comparison, at 1460Hz-1540Hz and 1840Hz-2000Hz, the periodic arrangement after merging the isolation units will produce a band gap due to Bragg scattering, and the structural vibration attenuation effect is far better than the interval arrangement method.

[0087] The specific working mode of the present invention is: when the vibration of the pipeline 6 is transmitted to the vibration isolation unit, the support seat body 1 undergoes shear and tensile deformation, and at the same time the constraint layer produces deformation to enhance the energy attenuation effect; when the amplitude is small, energy is mainly consumed through the bending deformation of the support seat body 1; when the amplitude is large, the flexible support seat body 1 consumes energy through its own flexible deformation and the deformation of multiple vibration isolation layers. In the axial direction, that is, the y-axis direction, the support seat body 1 produces bending deformation, shear deformation in the z-axis direction, and shear and bending deformation in the x-axis direction, dissipating energy under the coupling of vibration and deformation.

[0088] [Example 3]

[0089] This embodiment is used to design the structure of a multi-dimensional and multi-mode pipeline vibration isolation device in Example 1 and Example 2, and includes the following steps:

[0090] S1. Determine the design frequency f of ground vibration excitation on pipeline 6 in all directions x 、f y 、f z Wherein the axial direction along the pipe 6 is the y-axis direction, the horizontal radial direction along the pipe 6 is the x-axis direction, and the horizontal radial direction perpendicular to the pipe 6 is the z-axis direction;

[0091] S2. Determine different vibration isolation forms of the support base body 1 caused by the vibration of the pipeline 6 in various directions; the vibration isolation form is the deformation mode of the support base body 1;

[0092] When the pipe 6 excites the support base body 1 in the x-axis direction, the vibration isolation form of the support base body 1 is shear and bending deformation;

[0093] When the pipe 6 excites the support base body 1 in the y-axis direction, the vibration isolation form of the support base body 1 is bending deformation;

[0094] When the pipe 6 excites the support base body 1 in the z-axis direction, the vibration isolation form of the support base body 1 is shear deformation;

[0095] S3. Determine the stiffness K of the pipeline 6 in each direction x , K y , K z Then the circular frequency ω of the support base body 1 in each direction is obtained x 、ω y 、ω z ;

[0096] S4, by design frequency f x 、f y 、f z , the circular frequency ω of the support body 1 in each direction x 、ω y 、ωz and the stiffness K of the pipe 6 in all directions x , K y , K z Obtaining geometric parameters of the support base body 1;

[0097] S5. Determine the mass of mass block 2.

[0098] As an optional embodiment, the stiffness K of the pipe 6 in each direction in S3 is x , K y , K z Get the circular frequency ω of the support base body 1 in each direction x 、ω y 、ω z The method comprises the following steps:

[0099] S31. Calculate the stiffness K of pipeline 6 in each direction x , K y , K z :

[0100] The stiffness K of the pipe 6 in the x-axis direction x for:

[0101] K x =(2~6)K z

[0102] The stiffness K of the pipe 6 in the y-axis direction y for:

[0103] K y =2A L m y G / H

[0104] in,

[0105] A L =L·B

[0106] m y =1 / (1+0.29(H / L) 2 )

[0107] Wherein, G is the shear elastic modulus of the material selected for the support seat body 1, H is the vertical height of the cross section of the support portion 12, m y is the calculation coefficient, B is the cross-sectional width of the support portion 12, L is the front width of the support portion 12, A L is the horizontal cross-sectional area of the supporting portion 2 12;

[0108] The stiffness K of the pipe 6 in the z-axis direction z for:

[0109] K z=4πHG / ln(R H / R B )

[0110] Where m is the mass of the support body 1, R H R is the distance from the connection between the second support portion 12 and the third support portion 13 to the center line of the cross section of the support base body 1; B is the projection width of the supporting portion 2 12 on the ground;

[0111] S32. Obtain the stiffness K of the pipeline 6 in each direction x , K y , K z and the circular frequency ω of the support body 1 in each direction x 、ω y 、ω z :

[0112] Circular frequency ω of pipe 6 in the x-axis direction x for:

[0113]

[0114] Circular frequency ω of pipe 6 in the y-axis direction y for:

[0115]

[0116] Circular frequency ω of pipe 6 in the z-axis direction z for:

[0117]

[0118] As an optional implementation, in S4, the frequency f is designed x 、f y 、f z , the circular frequency ω of the support body 1 in each direction x 、ω y 、ω z and the stiffness K of the pipe 6 in all directions x , K y , K z The method for obtaining the geometric parameters of the support base body 1 comprises the following steps:

[0119] S41, according to the design frequency f x 、f y 、f z , the circular frequency ω of pipe 6 in the x-axis, y-axis and z-axis directions x 、ω y 、ω z The stiffness K of the pipe 6 in all directions x , K y, K z Get the stiffness K x , K y , K z With the design frequency f x 、f y 、f z The relationship:

[0120] K n =4π 2 mf n 2

[0121] Where n = x, y, z;

[0122] S42, combined with the stiffness K of pipe 6 in the z-axis direction in S31 z The geometric parameters H and R of the support body 1 can be obtained H 、R B Relationship with design frequency fz:

[0123] H / ln(R H / R B )=πmf z 2

[0124] S43, combined with the stiffness K of pipe 6 in the y-axis direction in S31 y The geometric parameters B, L, H and design frequency f of the support body 1 can be obtained y Relationship:

[0125] BL 3 / (HL 2 +0.29H 3 )=2π 2 mf y 2 / G

[0126] As an optional implementation, the method for determining the mass of the mass block 2 in S5 includes the following steps:

[0127] S51, determine the relationship between the resonance frequency f of the support rod 8 and the mass of the mass block 2:

[0128] The two ends of the support rod 8 are fixed to the support portion 12 through the through hole 7. The motion equation of the support rod 8 is:

[0129]

[0130] After separating the variables:

[0131] d 4 y(x) / d 4 xk 4 y(x)=0

[0132] Wherein, A is the cross-sectional area of the support rod 8, l is the length of the support rod 8, ρ is the density of the support rod 8, EI is the bending stiffness of the support rod; k and a are both calculation coefficients:

[0133] k 4 =ω 2 / a 2

[0134] a 2 =EI / (ρA)

[0135] After calculation, the relationship between the resonant frequency f of the support rod 8 and the density ρ of the support rod 8 is obtained:

[0136]

[0137] S52. Since the mass block 2 is connected to the support rod 8, the mass of the mass block 2 is adjusted to adjust the mass of the support rod 8, thereby adjusting the resonance frequency of the support rod 8 and the resonance frequency of the entire device.

[0138] The present invention has high elastic dissipation characteristics, and the constraint layer has expansion and energy dissipation characteristics. Generally speaking, it has a good energy dissipation effect, and forms a resonance band gap through the mass block to dissipate the vibration propagation energy. The device has a simple structure, good vibration reduction effect, and a wide operating frequency band. It does not require additional external energy supply, works stably, and has a long service life. It uses the support base for building the pipeline as the basis, and does not require additional load on the circumference of the pipeline. When the excitation amplitude is small, it is mainly the viscoelastic deformation of the support base body 1 that provides corresponding vibration isolation stiffness for the structure. When the excitation amplitude is large, the constraint layer expands and deforms to consume vibration energy, so as to further realize the vibration isolation capability of the structure.

[0139] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "installed," "provided with," "mounted / connected," and "connected" should be understood in a broad sense. For example, "connected" can mean a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be internal communication between two components. Those skilled in the art will be able to understand the specific meanings of the above terms in the present invention in specific circumstances.

[0140] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to these embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the appended claims and their equivalents.

Claims

1. A multi-dimensional and multi-mode pipeline vibration isolation device, characterized in that: The invention comprises a plurality of vibration isolation units for supporting a pipe (6), wherein the vibration isolation units comprise a support seat body (1) and a plurality of vibration isolation layers arranged on the support seat body (1); the support seat body (1) comprises a support portion 1 (11), a support portion 2 (12) and a connecting portion (13); the support portion 2 (12) is a two-stage type and is symmetrically arranged about the support portion 1 (11), and the two sections of the support portion 2 (12) are respectively connected to the connecting portion (13); the plurality of vibration isolation layers comprise a support layer (3) covering the support portion 1 (11), a constraint layer (4) and a damping layer (5) covering the support portion 2 (12) in sequence; a through hole (7) is provided on the support portion 2 (12), a support rod (8) is transversely arranged in the through hole (7), both ends of the support rod (8) are connected to the support portion 2 (12), and a mass block (2) is sleeved on the middle section of the support rod (8); The support seat body (1), the damping layer (5) and the support rod (8) are all made of viscoelastic damping materials; the mass block (2) is a metal block; and the support layer (3) and the constraint layer (4) are metal plates.

2. The multi-dimensional and multi-mode pipeline vibration isolation device according to claim 1, characterized in that: The support part 1 (11), the support part 2 (12) and the connecting part (13) are integrally connected, and the cross section of the support part 1 (11), the plurality of support parts 2 (12) and the plurality of connecting parts (13) after being integrally connected is a trapezoidal structure, the support part 1 (11) is arranged along the plane where the top edge of the trapezoid is located, the support part 2 (12) is arranged along the plane where the two waist edges of the trapezoid are located, and the connecting part (13) is integrally connected to the bottom end of the support part 2 (12); the connecting part (13) is provided with a plurality of bolts for fixing to the ground.

3. The multi-dimensional and multi-mode pipeline vibration isolation device according to claim 1, characterized in that: The support portion 1 (11) and the support layer (3) are bent downward, and the curvature of the bending is the same as the curvature of the outer diameter of the pipe (6); the support portion 2 (12) and the constraint layer (4) and the damping layer (5) covering the support portion 2 (12) are all bent toward the center of the support seat body (1).

4. The multi-dimensional and multi-mode pipeline vibration isolation device according to claim 3, characterized in that: The thickness of the support layer (3), the constraint layer (4) and the damping layer (5) is 1.5 mm to 5 mm.

5. The multi-dimensional and multi-mode pipeline vibration isolation device according to claim 1, characterized in that: The plurality of vibration isolation units are closely connected or spaced apart from each other.

6. A design method for a multi-dimensional and multi-mode pipeline vibration isolation device according to any one of claims 1 to 5, characterized in that: The following steps are involved: S1. Determine the design frequency ƒ of the ground vibration excitation on the pipeline (6) in all directions x 、ƒ y 、ƒ z ; The axial direction along the pipeline (6) is the y-axis direction, the horizontal radial direction along the pipeline (6) is the x-axis direction, and the horizontal radial direction perpendicular to the pipeline (6) is the z-axis direction; S2, determining different vibration isolation forms of the support base body (1) caused by the vibration of the pipeline (6) in various directions; the vibration isolation form is the deformation mode of the support base body (1); When the pipe (6) generates an excitation on the support seat body (1) in the x-axis direction, the vibration isolation form of the support seat body (1) is shear and bending deformation; When the pipe (6) generates an excitation on the support seat body (1) in the y-axis direction, the vibration isolation form of the support seat body (1) is bending deformation; When the pipeline (6) generates an excitation on the support seat body (1) in the z-axis direction, the vibration isolation form of the support seat body (1) is shear deformation; S3. Determine the stiffness of the pipe (6) in each direction K x 、 K y 、 K z Then the circular frequency of the support base body (1) in each direction is obtained ω x 、 ω y 、 ω z ; S4, by design frequency ƒ x 、ƒ y 、ƒ z , the circular frequency of the support body (1) in each direction ω x 、 ω y 、 ω z and the stiffness of the pipe (6) in all directions K x 、 K y 、 K z Obtaining geometric parameters of the support seat body (1); S5. Determine the mass of the mass block (2).

7. The design method of the multi-dimensional and multi-mode pipeline vibration isolation device according to claim 6 is characterized in that: Stiffness in all directions through the pipe (6) in S3 K x 、 K y 、 K z Get the circular frequency of the support base body (1) in each direction ω x 、 ω y 、 ω z The method comprises the following steps: S31. Calculate the stiffness of the pipe (6) in all directions K x 、 K y 、 K z : The stiffness of the pipe (6) in the x-axis direction K x for: The stiffness of the pipe (6) in the y-axis direction K y for: in, in, G is the shear elastic modulus of the material selected for the support body (1), H is the vertical height of the cross section of the support part 2 (12), To calculate the coefficient, B is the cross-sectional width of the support portion 2 (12), L is the front width of the support part 2 (12), A L is the horizontal cross-sectional area of the support portion 2 (12); The stiffness of the pipe (6) in the z-axis direction K z for: in, m is the mass of the support body (1), R H The distance from the connection point between the second support portion (12) and the connection portion (13) to the center line of the cross section of the support seat body (1); R B is the projection width of the support part 2 (12) on the ground; S32. Obtain the stiffness of the pipe (6) in each direction K x 、 K y 、 K z The circular frequency of the support body (1) in each direction ω x 、 ω y 、 ω z : in, ω x is the circular frequency of the pipe (6) in the x-axis direction, ω y is the circular frequency of the pipe (6) in the y-axis direction, ω z is the circular frequency of the pipe (6) in the z-axis direction.

8. The design method of the multi-dimensional and multi-mode pipeline vibration isolation device according to claim 6, characterized in that: S4 is designed to pass the frequency ƒ x 、ƒ y 、ƒ z , the circular frequency of the support body (1) in each direction ω x 、 ω y 、 ω z and the stiffness of the pipe (6) in all directions K x 、 K y 、 K z The method for obtaining the geometric parameters of the support seat body (1) comprises the following steps: S41, according to the design frequency ƒ x 、ƒ y 、ƒ z , the circular frequency of the pipeline (6) in the x-axis, y-axis, and z-axis directions ω x 、 ω y 、 ω z The stiffness of the pipe (6) in all directions K x 、 K y 、 K z Get stiffness K x 、 K y 、 K z and design frequency ƒ x 、ƒ y 、ƒ z The relationship: in, ; S42, combined with the stiffness of the pipe (6) in the z-axis direction in S31 K z The geometric parameters of the support body (1) can be obtained H 、 R H 、 R B Relationship with design frequency ƒz: S43, combined with the stiffness of pipe (6) in S31 in the y-axis direction K y The geometric parameters of the support body (1) can be obtained 、 、 and design frequency ƒ y Relationship: Among them, ƒ y is the design frequency.

9. The design method of the multi-dimensional and multi-mode pipeline vibration isolation device according to claim 6, characterized in that: The method for determining the mass of the mass block (2) in S5 comprises the following steps: S51. Determine the relationship between the resonant frequency ƒ of the support rod (8) and the mass of the mass block (2): The two ends of the support rod (8) are fixed to the support part 2 (12) through the through hole (7). The motion equation of the support rod (8) is: After separating the variables: in, is the cross-sectional area of the support rod (8), is the length of the support rod (8), is the density of the support rod (8), is the bending stiffness of the support rod; k and a All are calculation coefficients: After calculation, the resonance frequency ƒ of the support rod (8) and the density of the support rod (8) are obtained. The relationship: S52. Since the mass block (2) is connected to the support rod (8), the mass of the support rod (8) is adjusted by adjusting the mass of the mass block (2), thereby adjusting the resonant frequency of the support rod (8) and the resonant frequency of the entire device.

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