High-load-bearing low-frequency vibration isolation corrugated pipe

Abstract

The application discloses a high-load low-frequency vibration isolation corrugated pipe, which is integrally formed by a plurality of tubular units, and the tubular unit wall comprises a hoop ring, a rubber coating and a bearing plate; the rubber coating is a tubular shell with one or two wave crest structures, the bearing plate is a segmented structure and is uniformly arranged in a wave crest mode along the inner wall structure of the rubber coating; the number of the hoop rings is consistent with the number of gaps between the bearing plates, the hoop rings are arranged outside the rubber coating and correspond to the gap positions, and the axial span of the hoop ring is greater than the width of the gap. The application can realize wide vibration isolation performance in a low frequency band and good vibration reduction and noise reduction performance in a medium and high frequency band.

Description

Technical Field

[0001] This invention relates to the field of seawater pipeline technology, specifically to a high-load-bearing, low-frequency vibration-isolation corrugated pipeline. Background Technology

[0002] Current technology typically uses thin-walled cylindrical pipes as the connecting structure to connect two long pipelines. This connecting structure needs to operate normally under high internal pressure conditions (e.g., 10 MPa). As the internal pressure increases, the thin-walled pipe needs to be thickened to meet the pressure requirements, which leads to an increase in the axial stiffness of the thin-walled pipe. When the load requirement is 10 MPa, the corresponding axial stiffness of the thin-walled pipe will increase. Secondly, thin-walled pipes lack microstructure design, and their axial stiffness is closely related to the vibration isolation effect of the pipeline; the greater the axial stiffness, the worse the vibration isolation effect. Summary of the Invention

[0003] In view of this, the present invention provides a high load-bearing low-frequency vibration isolation corrugated pipe that can achieve a wide vibration isolation performance in the low-frequency range and good vibration reduction and noise reduction performance in the mid-to-high frequency range.

[0004] The technical solution adopted in this invention is as follows:

[0005] A high load-bearing, low-frequency vibration-isolation corrugated pipe is composed of several tubular units integrated into one unit. The pipe wall of each tubular unit includes a hoop, a rubber coating, and a load-bearing plate.

[0006] The coating is a tubular shell with one or two corrugated peaks, and the bearing plate is a segmented structure with corrugated peaks evenly arranged along the inner wall of the coating. The number of hoop rings is the same as the number of gaps between the bearing plates. The hoop rings are set outside the coating and correspond to the gap positions, and the axial span of the hoop rings is greater than the gap width.

[0007] Furthermore, the outer surface of the rubber coating has a pre-drilled annular groove for installation with the hoop, and the two are connected by a snap-fit ​​mechanism.

[0008] Furthermore, both the hoop and the bearing plate are made of aluminum.

[0009] Furthermore, the coating is made of rubber material.

[0010] Furthermore, the bearing plates at both ends are located in the same vertical plane.

[0011] Furthermore, the farthest end of the bearing plate is 230mm from the central axis.

[0012] Furthermore, the coating has a wave-shaped structure, and the supporting plate has at least four segments.

[0013] Furthermore, the coating has two wave crests, the inner diameter of the trough between the two wave crests is not less than the inner diameter of the two end ports, and the bearing plate has at least six segments.

[0014] Beneficial effects:

[0015] 1. This invention achieves high internal pressure bearing capacity by reinforcing the outer ring and setting the internal bearing plate. The corrugated pipe structure is filled with a soft sound-insulating material with rubber coating in the middle, resulting in a wide bandwidth (local resonance bandwidth generated by local oscillators) in the low-frequency range. Therefore, compared with ordinary circular pipes, it has better vibration isolation effect in the low-frequency range and can achieve a wider range of vibration isolation performance. Due to the low stiffness of the structure, it achieves good vibration reduction and noise reduction performance in the mid-to-high frequency range. The corrugated pipe structure is reasonably designed, simple in configuration and easy to manufacture, and can also meet the high internal pressure bearing capacity requirements of actual use conditions. Therefore, the pipe structure of this invention has a wide range of applicability.

[0016] Secondly, the load-bearing plate has a segmented structure and uses a single-peak design to further reduce the axial stiffness. This ensures both an internal pressure bearing capacity of 10MPa and a relatively low overall axial stiffness, thereby ensuring good low-frequency bandgap vibration isolation performance.

[0017] 2. In this invention, the rubber coating and the hoop are connected by a snap-fit ​​mechanism. An annular groove is reserved on the outside of the rubber coating to fit the hoop. This allows for a better connection of the external hoop, ensuring the integrity of the whole structure and minimizing the possibility of the external hoop separating from the overall structure.

[0018] 3. The upper and lower end faces of the bearing plate of this invention are in the same vertical plane, which can ensure that the structure is in the most stable state.

[0019] 4. The coating of this invention has two wave crests and the trough between the two wave crests is a curved surface design, which increases the tensile and compressive space of the structure. Secondly, the inner diameter of the trough is not less than the inner diameter of the two ends, which can prevent the fluid from directly impacting the trough when the fluid flows through the pipeline. Attached Figure Description

[0020] Figure 1 This is a front view of a tubular unit according to an embodiment of the present invention.

[0021] Figure 2 This is a front view of a tubular unit according to an embodiment of the present invention.

[0022] Figure 3 This is a front view of the cross-section of the rubber coating in Example 1.

[0023] Figure 4 This is a front view of the cross-section of the rubber coating in Example 1.

[0024] Figure 5 This is a front view of the coating process in Example 1.

[0025] Figure 6 This is a front view of the coating process in Example 1.

[0026] Figure 7 This is a front sectional view of the support plate in Embodiment 1.

[0027] Figure 8 This is a cross-sectional front view of the support plate in Embodiment 1.

[0028] Figure 9 This is the front view of the support plate in Embodiment 1.

[0029] Figure 10 This is a front view of the support plate in Embodiment 1.

[0030] Figure 11 This is a front view of the hoop ring in Example 1.

[0031] Figure 12 This is a front view of the hoop ring in Example 1.

[0032] Figure 13 This is a front view of the hoop ring in Example 1.

[0033] Figure 14 This is a front view of the hoop ring in Example 1.

[0034] Figure 15 This is the pipeline vibration transmission curve in this embodiment.

[0035] Figure 16 This is the pressure stiffness curve for this embodiment.

[0036] Figure 17 This is a front view of the tubular unit in Embodiment 2 of the present invention.

[0037] Figure 18 This is a front view of the tubular unit in Embodiment 2 of the present invention.

[0038] Figure 19 This is a front view of the cross-section of the rubber coating in Example 2.

[0039] Figure 20 This is a front view of the cross-section of the rubber coating in Example 2.

[0040] Figure 21 This is a front view of the coating process in Example 2.

[0041] Figure 22 This is a front view of the coating process in Example 2.

[0042] Figure 23 This is a sectional front view of the support plate in Embodiment 2.

[0043] Figure 24 This is a cross-sectional front view of the support plate in Embodiment 2.

[0044] Figure 25 This is a front view of the support plate in Embodiment 2.

[0045] Figure 26 This is a front view of the support plate in Embodiment 2.

[0046] Figure 27 This is a front view of the hoop ring in Example 2.

[0047] Figure 28 This is a front view of the hoop ring in Example 2.

[0048] Figure 29 This is the front view of the hoop ring in Example 2.

[0049] Figure 30 This is a front view of the hoop ring in Example 2.

[0050] Figure 31 This is the pipeline vibration transmission curve in Example 2.

[0051] Figure 32 This is the pressure stiffness curve for Embodiment 2.

[0052] Among them, 1-hoop ring, 2-rubber coating, 3-bearing plate. Detailed Implementation

[0053] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0054] This invention provides a high-load-bearing, low-frequency vibration-isolation corrugated conduit, which is integrally composed of several tubular units. The tube wall of each tubular unit includes a hoop 1, a rubber coating 2, and a load-bearing plate 3, as shown below. Figure 1 , Figure 2 , Figure 17 , Figure 18 As shown.

[0055] The coating 2 is a tubular shell with one or two corrugated peaks, and the outer surface of the coating 2 has a pre-reserved annular groove for installation with the hoop 1.

[0056] The support plate 3 has a segmented structure, with single-peaked uniformly arranged inside the coating 2; the support plates 3 at both ends are in the same vertical plane. When the coating 2 has one peak structure, the support plate 3 has at least four segments. When the coating 2 has two peak structures, the support plate 3 has at least six segments.

[0057] The number of hoop rings 1 is the same as the number of gaps between the bearing plates 3. The hoop rings 1 are set outside the rubber coating 2 and the two are connected by a snap-fit. The position of the hoop rings 1 corresponds to the position of the gap, and the axial span of the hoop rings 1 is greater than the width of the gap.

[0058] In Example 1, as Figures 3-6As shown, the rubber coating 2 has a corrugated structure. The rubber coating 2 is made of rubber material with a density of 1150 kg / m³. 3 The Young's modulus is 7.8e6 MPa, and the Poisson's ratio is 0.47. The overall thickness of the rubber coating 2 is 45 mm. At this thickness, the structure has low axial stiffness and good vibration isolation performance. The rubber coating 2 is injected between the bearing plate 3 and the hoop 1, and the gap in the bearing plate 3 is also filled with rubber coating 2.

[0059] Let the length of the tubular unit be L, the inner diameter of the pipe be a, the length of the straight section at the port be b, the radius of the circle corresponding to the arc of the bearing plate 3 be r, and the degree measure of the arc be 2θ. Then θ satisfies

[0060]

[0061] arctan((L-2b) / 300)<θ<1800

[0062] like Figures 7-10 As shown, the support plate 3 consists of six sections made of aluminum with a thickness of 5mm, and the gap width between the support plates 3 is 4mm. The upper support plate 3 has a 16mm long smooth interface for connection with the flange to ensure the applicability of the structure. The farthest end of the middle support plate 3 is 230mm from the central axis, which is also the most stable arc under the condition of resisting internal pressure of 10MPa, ensuring both the low stiffness characteristics of the single-peak pipeline and the internal pressure resistance performance of the structure.

[0063] like Figures 11-14 As shown, there are five hoop rings 1, forming a complete circular ring. The two end hoop rings 1 are non-standard rectangular with a quadrilateral cross-section. The top and bottom edges are straight, while the left and right edges are curved. This design allows for a snap-fit ​​connection with the gap left by the rubber-coated part 2, and also provides complementary bearing capacity with the gap of the bearing plate 3. The outer hoop rings 1 not only ensure the overall resistance to internal pressure but also achieve the goal of low stiffness. The three middle hoop rings 1 use a standard rectangular design. The use of a stable design in non-stress concentration areas reduces stiffness and simplifies the design and manufacturing process.

[0064] When this embodiment is used in the field of seawater pipeline systems for ships, submarines, etc., damping is considered, and the rubber damping coefficient is set to 0.08. The pipeline vibration transmission curve is as follows. Figure 15 As shown. Under the condition of internal pressure bearing of 10MPa, the axial stiffness of the pressurization is calculated. In this embodiment, the axial stiffness under 10MPa pressurization is 2832.78 N / mm. Figure 16 As shown.

[0065] In Example 2, as Figures 19-22As shown, the rubber coating 2 has two corrugated structures. The inner diameter of the trough between the two corrugated structures is not less than the inner diameter at both ends. The trough is a curved surface structure that smoothly transitions with the corrugated structures on both sides. The overall thickness of the pipeline is 30mm, and the thickness of the rubber coating 2 is 26mm, made of rubber material.

[0066] like Figures 23-26 As shown, the bearing plate 3 consists of eight segments, made of 7075 aluminum, with a thickness of 4mm, and a gap width of 5mm. The curvature is designed considering two main aspects: first, low axial stiffness, requiring the curvature of bearing plate 3 to be as large as possible; second, bearing internal pressure, requiring the curvature of bearing plate 3 to be as small as possible. Let the length of the tubular unit be L, the inner diameter of the pipe be a, the length of the straight section at the end be b, the radius of the circle corresponding to the arc of bearing plate 3 be r, and the degree measure of the arc be 2θ. Then θ satisfies...

[0067]

[0068] arctan((L-4b) / 600)<θ<1800

[0069] like Figures 27-30 As shown, there are seven hoop rings 1, also made of 7075 aluminum. The thickness of hoop ring 1 is greater than 10mm to ensure the load-bearing capacity of the structure. The axial length of hoop ring 1 is greater than 5mm.

[0070] When this second embodiment is used in seawater pipeline systems for ships, submarines, etc., damping is considered, and the rubber damping coefficient is set to 0.05. The pipeline vibration transmission curve is as follows: Figure 31 As shown. Under the condition of internal pressure bearing of 10MPa, the axial stiffness of the pressurization is calculated. In this embodiment, the axial stiffness of 10MPa pressurization is 2785N / mm. Figure 32 As shown.

[0071] In summary, the above are merely preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-load-bearing, low-frequency vibration-isolation corrugated pipe, characterized in that, Used in seawater pipeline systems, it is composed of several tubular units integrated into one unit. The tubular unit wall includes a hoop, rubber coating, and a load-bearing plate. The coating is a tubular shell with one or two corrugated peaks, and the bearing plate is a segmented structure with corrugated peaks evenly arranged along the inner wall of the coating. The number of hoop rings is the same as the number of gaps between the bearing plates. The hoop rings are set outside the coating and correspond to the gap positions, and the axial span of the hoop rings is greater than the gap width. Low-frequency vibration isolation is achieved by generating a local resonant bandgap. When the coating has a wave-shaped structure, the bearing plate has at least four segments; When the coating has two wave crests, the inner diameter of the trough between the two wave crests is not less than the inner diameter of the two end ports, and the bearing plate has at least six segments.

2. The high-load-bearing, low-frequency vibration-isolation corrugated pipe as described in claim 1, characterized in that, The outer surface of the rubber coating has a pre-drilled annular groove for installation with the hoop, and the two are connected by a snap-fit ​​mechanism.

3. The high-load-bearing, low-frequency vibration-isolation corrugated pipe as described in claim 1, characterized in that, Both the hoop and the bearing plate are made of aluminum.

4. The high-load-bearing, low-frequency vibration-isolation corrugated pipe as described in claim 1, characterized in that, The coating is made of rubber.

5. The high-load-bearing, low-frequency vibration-isolation corrugated conduit as described in any one of claims 1-4, characterized in that, The bearing plates at both ends are in the same vertical plane.

6. The high-load-bearing, low-frequency vibration-isolation corrugated pipe as described in claim 5, characterized in that, The farthest end of the bearing plate is 230mm from the central axis.

Images