Pipe vibration damping structure

Abstract

The present invention relates to a pipe vibration damping structure that effectively controls circumferential vibration generated in a pipe in which an ultra-high-speed traveling body moves. A tube vibration damping structure according to one embodiment of the present invention comprises: a tube for the movement of a traveling body, the tube having a low pressure formed therein; an outer ring provided on the outside of the tube; and one or more damping members disposed between the outer ring and the tube.

Description

Technical Field

[0001] The present invention relates to a pipe vibration attenuation structure for effectively controlling the circumferential vibration generated by a traveling body in a pipe moving inside. Background Art

[0002] Generally, in ultra-high-speed train systems above 300km / h, two types of resistance need to be solved according to the speed. The development direction is to design an aerodynamic running body to reduce the geometrically increasing air resistance, and to introduce a magnetic levitation system to reduce the friction between the running body and the track.

[0003] However, since the Hyperloop Alpha Concept proposed a system that would introduce the conventional 1 atmosphere of pressure into a super-high-speed vacuum tube in a sealed tube at a pressure of 0.001 of the stratosphere level 50 kilometers above the ground, various attempts have been made to actually realize the system.

[0004] In these attempts, the system that suspends and propels the system through electromagnetics and mechanics is certainly important, but it is also important to realize the tube structure for maintaining a sub-vacuum state of about 0.001 atmosphere in the infrastructure that accounts for more than 50% of the initial investment cost.

[0005] The tube structure is a passageway in which the traveling body that transports passengers or goods moves. Therefore, it is set to be larger than the cross-sectional area of ​​the traveling body. The blockage ratio, which is usually expressed as the ratio of the traveling body cross-sectional area to the tube cross-sectional area, is 0.38~0.60. In the Hyperloop Alpha Concept proposed in 2012, the traveling body diameter was 1.38 meters, the tube diameter was 2.23 meters, and the blockage ratio was 0.38. However, the traveling body diameter of 1.38 meters is too high to stand, which is not conducive to the riding comfort of passengers. Therefore, in recent attempts by Virgin Hyperloop One and others, there is a trend of large-scale traveling body diameters of 2.4 meters and tube diameters of 3.66 meters.

[0006] Inside the tube, a magnetic levitation system is used to reduce frictional resistance, which is one of the resistances to travel. Since magnetic levitation is maintained by attraction, it is very important to periodically and accurately switch the attraction and repulsion of the magnetic field to maintain a constant interval between the guide rail and the traveling body.

[0007] However, since the spacing between the guide rails acts as a certain concave and convex, the traveling body will produce considerable vibrations when the speed increases, so it is essential to control the generated vibrations.

[0008] (Patent Document 1) Korean Patent Publication No. 10-2021-0152184 (published on December 15, 2021) Summary of the invention

[0009] 1. Technical issues to be resolved

[0010] The present invention is proposed to solve the above-mentioned problems, and its object is to provide a pipe vibration attenuation structure that can effectively control the circumferential vibration when the running body runs inside the pipe.

[0011] (II) Technical solution

[0012] In order to achieve the above object, the present invention provides a pipe vibration damping structure formed as follows.

[0013] A pipe vibration damping structure according to an embodiment of the present invention includes: a pipe forming a low pressure inside and used for movement of a traveling body; an outer ring disposed outside the pipe; and one or more damping components disposed between the outer ring and the pipe.

[0014] According to a tube vibration attenuation structure of one embodiment of the present invention, the outer ring is formed with a through hole penetrating along the thickness direction, the damping component is formed with a fixing groove, and the fixing groove is formed along the thickness direction from a surface close to the outer ring, and the tube vibration attenuation structure further includes: a fixing component, which is connected to the through hole and the fixing groove from the outside of the outer ring.

[0015] The pipe vibration damping structure according to one embodiment of the present invention further includes: an auxiliary component located between the outer ring and the damping component.

[0016] (III) Beneficial effects

[0017] Through the above structure, the present invention provides a method for effectively controlling the vibration in the circumferential direction when the traveling body travels at high speed in the tube used for the super high-speed rail, so that the interval between the guide rail located inside the tube and the traveling body remains constant, thereby stably maintaining the effect of the magnetic levitation system. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is a perspective view of a pipe vibration damping structure according to an embodiment of the present invention.

[0019] Figure 2 is a side view of a pipe vibration damping structure according to an embodiment of the present invention.

[0020] Figure 3 is a partially exploded view of a pipe vibration damping structure according to an embodiment of the present invention.

[0021] Figure 4An outer ring of a pipe vibration damping structure according to an embodiment of the present invention is shown, wherein (a) is a side view and (b) is a front view.

[0022] Figure 5 The figures are experimental results of vibration frequency and damping degree of conventional pipes and pipes according to the pipe vibration damping structure of the present invention in various vibration modes.

[0023] FIG6 is an experimental result showing the vibration frequency and damping degree of a conventional pipe and a pipe according to the pipe vibration attenuation structure of the present invention in each vibration mode according to the mode, Figure 6a is the result of Rayleigh Mode and Love Mode. Figure 6b It is the result of Breathing Mode and Bending Mode. DETAILED DESCRIPTION

[0024] Below, the specific embodiments of the present invention are described with reference to the accompanying drawings. However, the concept of the present invention is not limited to the proposed embodiments, and those skilled in the art who understand the concept of the present invention can easily propose other inventions or other embodiments included in the scope of the concept of the present invention by adding, changing or deleting other components within the same concept, and these should also be included in the scope of the concept of the present invention.

[0025] Figure 1 A perspective view showing a pipe vibration damping structure according to an embodiment of the present invention. Figure 2 A side view showing a tube vibration damping structure according to one embodiment of the present invention. Figure 3 An exploded view showing a pipe vibration damping structure according to one embodiment of the present invention, showing only a portion. Figure 4 The figure shows the appearance of an outer ring according to an embodiment of the present invention, wherein (a) is a side view and (b) is a front view.

[0026] The pipe vibration damping structure according to the present invention includes a pipe 10, an outer ring 20, and a damping member 30. In addition, a fixing member 40 and an auxiliary member 50 may be further included.

[0027] The pipe 10 according to the present invention forms a low pressure inside and is formed to move a traveling body.

[0028] Low pressure is formed inside the tube 10. When the pressure outside the tube 10 is 1 atm (about 101 kPa, 1 bar) atmospheric pressure, low pressure means that the pressure inside the tube is less than 10 kPa (0.1 bar), and may be a pressure close to vacuum.

[0029] For example, the low pressure may be 1 kPa (0.01 bar or 10 mbar), 500 Pa (5 mbar), 200 Pa (2 mbar), or 100 Pa (1 mbar). In addition, the case of a lower pressure than this is also included.

[0030] In the following description, 0.001 atm, or about 100 Pa (1 mbar), is used as a reference, but all the low pressure conditions mentioned above are included.

[0031] When exposed to a sub-vacuum state or a state close to a vacuum, the gas trapped inside will be released, resulting in pores, surface peeling, etc. Therefore, in order to prevent this phenomenon, it can be formed from a material with a low outgassing rate.

[0032] The material of the pipe 10 may be concrete, polymer composite material, steel, etc. In particular, steel is excellent in yield strength and tensile strength and has an excellent degassing rate of about 0.001 atm, and thus can be used as the material of the pipe 10 .

[0033] An outer ring 20 may be disposed outside the tube 10 .

[0034] In order to improve the damping ratio of the tube 10, an outer ring 20 is provided on the outer side of the tube 10 and arranged along the circular cross section of the tube. The outer ring 20 may be formed of steel. The outer ring 20 may be formed of various materials, but like the tube 10, may be formed of steel and may play a mass role in the tube structure.

[0035] According to an embodiment of the present invention, one or more outer rings 20 may be provided. In addition, the outer rings 20 may be located at the center and both ends of the tube 10 .

[0036] When there is one, it can be located only in the center, or in at least one of the two ends. It can also be located only in the two ends, or in the center and one of the two ends, so as to be located in two places. In addition, it can be located in three parts, namely, the two ends and the center.

[0037] That is, the outer rings 20 may be provided in a selected combination of positions among the central portion, the first end portion, and the second end portion of the tube 10 , and one to three outer rings 20 may be provided.

[0038] When the outer ring 20 is provided, since it acts as a mass in this part, the displacement caused by the vibration generated when the running body moves inside can be effectively reduced. Therefore, the outer ring 20 is located outside the tube 10, and while acting as a mass, it can also play a role of reinforcement to prevent vibration.

[0039] The outer ring 20 may be disposed at a distance from the tube 10 on the outside of the tube 10. For example, the outer ring 20 may be disposed at a distance of 3% to 5% of the outer diameter of the tube 10.

[0040] The outer ring 20 is disposed at a predetermined distance from the pipe 10 , and a damping member 30 described below may be disposed in a space therebetween.

[0041] If the outer ring 20 is spaced apart from the tube 10 by a predetermined distance or more, the attenuation efficiency is reduced and the circumference of the outer ring 20 is increased. Therefore, considering the attenuation efficiency and the circumference of the outer ring 20, the spaced apart distance may be formed at 3% to 5% of the outer diameter of the tube 10.

[0042] However, the spacing distance is not limited to the above, as long as the tube 10 and the outer ring 20 are spaced apart to form a stacked structure of the tube 10 , the damping member 30 described below, and the outer ring 20 .

[0043] For the outer ring 20 according to one embodiment of the present invention, the thickness of the outer ring 20 is not limited, but can be formed to be greater than the thickness of the tube 10. For example, the outer ring thickness d can be 2 to 4 times the thickness of the tube 10.

[0044] The local rigidity and the control of relative displacement can be adjusted by adjusting the outer ring thickness d based on the thickness of the tube 10. When the outer ring thickness d is kept 2 to 4 times the thickness, the local rigidity will be greater and the relative displacement can be effectively controlled by the outer ring 20.

[0045] However, the thickness is not limited to the above, and may be formed differently according to the design of the outer ring 20 and the vibration attenuation structure.

[0046] The outer ring width W is formed to be smaller than the length of the tube 10 based on the total length of the tube 10. For example, the outer ring width W may be formed to be 2% to 5% of the total length of the tube 10 based on the total length of the tube 10.

[0047] By forming the outer ring with a predetermined width, the damping member 30 described below is stably arranged to effectively perform damping. The outer ring width W can be set differently according to the design, and is not limited to the above-mentioned value.

[0048] The outer ring 20 is not limited to the shape described above, as long as it is arranged along the circumference of the outer side of the tube 10, it can include a polygonal annular component whose cross-section is a triangle or a quadrilateral, an annular component with at least a portion open, or an annular component with at least a portion protruding or recessed.

[0049] One or more damping members 30 are provided between the outer ring 20 and the tube 10. In addition, when multiple damping members 30 are provided, they can be provided at a predetermined interval in the circumferential direction. When multiple damping members 30 are provided, even if the predetermined interval is not maintained, different setting intervals can be provided according to the design, and vertical symmetry or left-right symmetry can be provided. The damping member 30 is not limited to the above-mentioned setting, as long as it is provided between the outer ring 20 and the tube 10.

[0050] The damping member 30 may be configured to be located between the outer ring 20 and the tube 10 to fill the space between the two members, and may effectively control minute displacement changes.

[0051] The damping member 30 may be formed in a rectangular parallelepiped shape having a height shorter than a length and a width, but is not limited to the above shape.

[0052] The damping member 30 is located between the outer ring 20 and the tube 10 , and can play a role in attenuating vibrations generated by the tube 10 .

[0053] The outer ring 20 may be formed of a member having relatively high strength and low elasticity. For example, it may be formed of steel. In contrast, the damping member 30 may be composed of an elastic material and a high-viscosity material. The damping member 30, as an elastomer, may be formed by mixing the elastic material and the high-viscosity material in a uniform or non-uniform state.

[0054] However, the damping member 30 is not limited to a prescribed shape or material, but includes all configurations that can play a damping role between the tube 10 and the outer ring 20 .

[0055] The elastic coefficient of the damping member 30 according to an embodiment of the present invention may be smaller than the elastic coefficient of the tube, for example, 0.001 to 0.01 times the elastic coefficient of the tube 10 .

[0056] By reducing the elastic coefficient of the damping member 30 to 0.001 to 0.01 times the elastic coefficient of the tube 10, elastic displacement can be caused to occur better than the tube 10. In this case, energy is easily absorbed and vibration can be effectively controlled.

[0057] According to an embodiment of the present invention, the loss factor of the damping member 30 may be 100 to 200 times greater than the loss factor of the tube 10 .

[0058] Loss factor attenuation is the inherent attenuation of a material measured when it is subjected to dynamic loading and is usually expressed as the ratio of the energy dissipated per unit volume per arc of vibration to the maximum deformation energy per unit volume.

[0059] The material of the damping member 30 may be determined so that the loss coefficient attenuation of the damping member 30 is 100 to 200 times greater than the loss coefficient attenuation of the tube 10. As described above, when there is a loss coefficient attenuation of 100 to 200 times and vibration is transmitted to the damping member 30, a damping effect may be rapidly generated.

[0060] The strength of the damping member 30 according to an embodiment of the present invention may be smaller than the strength of the outer ring 20. For example, the strength of the damping member 30 may be 0.01 to 0.1 times greater than the strength of the outer ring 20.

[0061] Unlike the outer ring 20, the damping member 30 is an easily replaceable member, so the damping member 30 can be formed to have a strength less than that of the outer ring 20, and can be formed to be 0.01 to 0.1 times the strength of the outer ring 20. However, since the damping member 30 is a replaceable configuration, its strength is not limited in consideration of this point.

[0062] The damping member 30 only needs to be located between the outer ring 20 and the tube 10 while playing a damping role. Since the strength is intended to satisfy the characteristic of not being easily damaged while playing a damping role, the strength is not limited to the above.

[0063] In addition, when a plurality of damping members 30 according to an embodiment of the present invention are provided, they may be configured to be provided at predetermined intervals or uneven intervals in the circumferential direction, and when the damping members 30 are provided, the sum of the areas intersecting with the tube 10 is 0.3% to 1.0% of the outer surface area of ​​the tube 10.

[0064] The damping component 30 arranged in the circumferential direction based on the outer surface area of ​​the tube 10 plays a role in transferring and attenuating energy by close contact between the tube 10 and the outer ring 20. Therefore, in order to transmit the vibration generated in the tube 10, it may be beneficial to transmit it through a large area, but it can be determined by considering the displacement change caused by the vibration of the damping component 30 itself.

[0065] The damping member 30 need not be applied to all surfaces of the tube 10, but the damping member 30 may be applied to intersect an area of ​​0.3% to 1.0% of the outer surface area of ​​the tube 10, thereby being economical and efficient and effectively controlling relative displacement locally.

[0066] The damping member 30 only needs to be located between the outer ring 20 and the tube 10 while playing a damping role, and the area can be changed according to the design degree such as the attenuation ratio to be satisfied by the damping member 30, and is not limited to the above area.

[0067] The pipe vibration damping structure according to the present invention may further include a fixing member 40 coupled to a fixing groove 31 formed on the damping member 30 from the outside of the outer ring 20 through the through hole 21 penetrating the outer ring 20 .

[0068] The outer ring 20 may be formed with a through hole 21 penetrating in the thickness direction so that the fixing member 40 can be coupled. In addition, the damping member 30 located between the pipe 10 and the outer ring 20 may be formed with a fixing groove 31, which may be formed in the thickness direction from a surface close to the outer ring 20 and not penetrated, and the fixing member 40 may be introduced into the fixing groove 31. Therefore, the fixing member 40 may be configured to pass through the through hole 21 from the outside of the outer ring 20 and be coupled to the fixing groove 31.

[0069] A thread is formed on the outside of the fixing member 40, so the shape formed inside the through hole 21 or the fixing groove 31 can be a shape corresponding to the thread of the fixing member 40. Alternatively, the fixing member 40 can be pressed into the through hole 21 and the fixing groove 31 and cannot fall off easily.

[0070] The structure of the fixing component 40 and the through hole 21 and the fixing groove 31 is not limited to the above-mentioned combination structure, but includes all structures that can be realized by ordinary technicians in this field.

[0071] According to one embodiment of the present invention, the fixing member 40 may be fixed while applying pressure to the damping member 30. In addition, the pressure applied by the fixing member 40 to the damping member 30 may be less than the strength of the damping member 30. This is because when the applied pressure is greater than the strength of the damping member 30, the damping member 30 may be damaged, and thus this is to avoid such a situation.

[0072] For example, the pressure applied by the fixing member 40 to the damping member 30 may be 40% to 60% of the strength of the damping member 30. When the fixing member 40 applies pressure to the damping member 30, about 40% to 60% of the strength of the damping member 30 is applied, so that the outer ring 20, the damping member 30 and the pipe 10 are fixed without separation without damaging the damping member 30, and by applying the above-mentioned pressure, the internal vibration is easily transmitted to the damping member 30 and the outer ring 20, and there may be a margin that can produce a certain degree of deformation.

[0073] When the fixing member 40 is formed in a shape such as a screw, the pressure transmitted can be adjusted by determining the number of rotations. Even if it is formed in other shapes, the pressure transmitted can be adjusted by adjusting the bonding force of the bonding.

[0074] According to an embodiment of the present invention, an auxiliary component 50 located between the outer ring 20 and the damping component 30 may be further included.

[0075] The auxiliary component 50 is a structure added to control the local pressure at the intersection of the damping component 30 and the fixing component 40. When the damping component 30 is deformed by pressure, it can fill the gap between the damping component 30 and the outer ring 20. Alternatively, it can also play a role in assisting the rigidity of the damping component 30.

[0076] For example, the auxiliary member 50 may be formed in a plate shape.

[0077] The auxiliary component 50 is aligned with the through hole 21 of the outer ring 20 and the fixing groove 31 of the damping component 30, and forms an auxiliary hole 51 formed therethrough, so that the fixing component 40 can be coupled to the auxiliary component 50 and the auxiliary hole 51. That is, the damping component 30, the auxiliary component 50, and the outer ring 20 can also be stacked and fixed in this order.

[0078] When the pressure transmitted through the fixing member 40 increases, the pressure can be adequately adjusted by increasing the size of the fixing member 40 itself. However, due to the width of the outer ring 20 and other conditions, increasing the size of the fixing member 40 may be structurally difficult or economically inefficient.

[0079] Therefore, in order to solve the above-mentioned problem, an auxiliary component 50 may be further included between the surface where the damping component 30 and the fixing component 40 intersect, that is, between the outer ring 20 and the damping component 30. Through the auxiliary component 50, it is possible to control the local pressure applied by the fixing component 40 to the damping component 30, and ensure that excessive pressure is not applied to a small area of ​​the damping component 30.

[0080] The auxiliary member 50 is not limited to a plate-shaped member, and includes structures of all shapes that disperse the pressure applied to the damping member 30 and effectively transmit it.

[0081] Figure 5 Experimental results of the vibration frequencies and damping degrees of a conventional pipe and a pipe having a pipe vibration damping structure according to the present invention in various vibration modes are shown.

[0082] The pipe 10 was set to have a diameter of 2.5 m, a thickness of 16 mm, and a length of 16 m. Modal analysis was performed to determine the natural vibration frequency of the structure and the shape of the vibration at the vibration frequency, thereby analyzing whether the structure resonated and obtaining the result.

[0083] The vibration modes of the tube 10 can be roughly classified into a Rayleigh Mode, a Love Mode, a Breathing Mode, and a Bending Mode.

[0084] Since the tube 10 having three degrees of freedom has three natural vibration frequencies, the result values ​​from the first mode to the third mode are obtained in the order of the lower natural vibration frequency. Figure 5 , only the result values ​​of the first mode are compared.

[0085] The test piece type of the existing pipe is marked as conventional, and the test piece type of the pipe 10 having the pipe vibration damping structure according to one embodiment of the present invention is marked as damping-enhanced pipe.

[0086] like Figure 5 As shown, it can be seen that the attenuation ratio of the damping enhanced tube has a larger value.

[0087] Figure 6a and Figure 6b The shapes of the natural modes of the conventional tube and the damping-enhanced tube in each vibration mode as well as their natural vibration frequencies and attenuation ratios are shown.

[0088] The bending mode is irrelevant to the case where the vibration direction is the circumferential direction, so in all modes except this mode, it can be seen that the damping ratio of the damping enhanced tube is significantly improved compared with the conventional tube. This is a common result from the first mode to the third mode.

[0089] In order to confirm the effect of the entire pipe system formed by connecting multiple pipes, a system formed by arranging multiple pipes 10 according to one embodiment of the present invention can be assumed. For example, a pipe structure of 80 m in total can be formed by connecting five pipes with a diameter of 2.5 m, a thickness of 16 mm, and a length of 16 m.

[0090] At this time, the two ends of the unconnected and open pipe connection structure are called E1 and E2, respectively. The running body travels from E1 to E2 at a speed of 1000 km / h inside the pipe, and the weight of the running body can be assumed to be 10 kN. The parts connected between the pipes are represented as P1 to P4 in sequence along the traveling direction, and the boundary conditions are assumed to be P3 as the fixed end and the other points as the movable ends.

[0091] Table 1 below is a table of response values ​​at various positions according to changes in attenuation ratio at various main frequencies, and shows only main values ​​of the results of vibration analysis performed under the above-mentioned conditions.

[0092] The points with the largest response values ​​of acceleration response and displacement response in the time domain, that is, the points with frequencies of 12.8 Hz and 15.2 Hz, are set as the main frequencies. In addition, the values ​​of acceleration response and displacement response in the frequency domain are marked representatively at this frequency, and the damping ratio is represented by DR in Table 1. The response ratio represents the ratio of the response value when the damping ratio is 1.0% to the response value when the damping ratio is 0.1%.

[0093]

Table 1

[0094]

[0095] The results of checking the response of the tube caused by the running of the running body at four points, namely P1 and P4 as the ends and P2 and P3 formed in the center, show that as the attenuation ratio increases, the displacement response and acceleration response decrease.

[0096] According to Table 1, as the attenuation ratio increases from 0.1% to 1.0%, the response ratio becomes 0.18 to 0.31, and thus the reduction ratio of the response is approximately 69% to 82%.

[0097] That is, as the attenuation ratio increases, the value of the vibration response becomes smaller, so that the vibration can be greatly improved to reduce the influence of the vibration.

[0098] In the case of a tube 10 provided with a tube vibration attenuation structure according to an embodiment of the present invention, the problem of the running body generating considerable vibration when the speed increases due to the concave-convex effect caused by the interval between the running body and the guide rail can be solved by increasing the attenuation ratio.

[0099] In the entire tube system, in order to reduce the friction resistance, which is one of the driving resistances, a magnetic suspension system will be used, and the attraction and repulsion of the magnetic field will be precisely converted periodically in the tube to maintain a constant interval between the guide rail and the running body, thereby maintaining the magnetic suspension system through attraction. At this time, the control of circumferential vibration helps to maintain the magnetic suspension system.

[0100] The tube vibration attenuation structure according to an embodiment of the present invention can also be applied to the case where the magnetic levitation system is maintained by utilizing the reaction force of the electrodynamic method, and the above-mentioned effect is the same in the case where the magnetic levitation system is maintained by utilizing the reaction force of the electrodynamic method.

[0101] That is, the pipe vibration damping structure according to one embodiment of the present invention greatly improves the damping ratio and effectively controls the vibration in the circumferential direction compared with the existing pipe, thereby providing an effect of easily maintaining the magnetic levitation system.

[0102] Although the present invention has been described above centering on the embodiments, the present invention is not limited to the above embodiments, and it is obvious that the present invention can be modified and implemented by a person skilled in the art without changing the technical concept of the present invention as claimed in the claims.

[0103] Description of Reference Numerals

[0104] 10: Tube

[0105] 20: External ring

[0106] 30: Damping components

[0107] 40: Fixed parts

[0108] 50: Auxiliary parts

[0109] W: External ring width

[0110] d: outer ring thickness

Claims

1. A pipe vibration attenuation structure, comprising: The tube forms a low pressure inside and is used for the movement of the traveling body; an outer ring disposed on the outside of the tube; as well as One or more damping components are disposed between the outer ring and the tube.

2. The pipe vibration damping structure according to claim 1, wherein: The outer ring is formed with a through hole penetrating in the thickness direction, The damping member is formed with a fixing groove, the fixing groove being formed in a thickness direction from a surface close to the outer ring, and, The pipe vibration damping structure further includes a fixing member coupled to the through hole and the fixing groove from an outside of the outer ring.

3. The pipe vibration damping structure according to claim 2, further comprising: An auxiliary component is located between the outer ring and the damping component.

4. The pipe vibration damping structure according to claim 1, wherein: The outer ring is formed from steel.

5. The pipe vibration damping structure according to claim 1, wherein: The thickness of the outer ring is 2 to 4 times the thickness of the tube.

6. The pipe vibration damping structure according to claim 1, wherein: The outer rings are spaced apart by a distance of 3% to 5% of the outside diameter of the tube.

7. The pipe vibration damping structure according to claim 1, wherein: The width of the outer ring is 2% to 5% of the length of the tube.

8. The pipe vibration damping structure according to claim 1, wherein: The elastic coefficient of the damping member is 0.001 to 0.01 times the elastic coefficient of the tube.

9. The pipe vibration damping structure according to claim 1, wherein: The loss coefficient attenuation of the damping member is 100 to 200 times greater than the loss coefficient attenuation of the tube.

10. The pipe vibration damping structure according to claim 1, wherein: In a state where the damping member is provided, a sum of areas intersecting the tube is 0.3% to 1.0% of an outer surface area of ​​the tube.

11. The pipe vibration damping structure according to claim 2, wherein: The pressure applied by the fixing member to the damping member is 40% to 60% of the strength of the damping member.

12. The pipe vibration damping structure according to claim 11, wherein: The strength of the damping member is 0.01 to 0.1 times the strength of the outer ring.

13. The pipe vibration damping structure according to claim 1, wherein: The outer ring is located at at least one of a central portion of the tube and both ends of the tube.

14. The pipe vibration damping structure according to claim 1, wherein: The damping member is provided in plurality and is arranged at predetermined intervals along the circumferential direction of the pipe.

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