Research on the influence of ring rib arrangement on vibration and acoustic radiation of cylindrical shell

Ronghui Ning1 , Zhenhai Zhang2

1College of Power Engineering, Naval University of Engineering, Wuhan, China

2College of Ship and Ocean, Naval University of Engineering, Wuhan, China

1Corresponding author

Vibroengineering PROCEDIA, Vol. 21, 2018, p. 172-177. https://doi.org/10.21595/vp.2018.20394
Received 21 November 2018; accepted 28 November 2018; published 13 December 2018

Copyright © 2018 Ronghui Ning, et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.
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Abstract.

Based on the thin shell theory and the three-dimensional Sono-elasticity theory, the finite element method is used to study the transmission and variation characteristics of the cylindrical shell, in the case of non-ribs, single ring ribs and multi-ring ribs. The influence of different ribbed forms on the acoustic radiation is also analyzed. The result shows that the ring rib structure can suppress the transmission of medium and high frequency vibration, and the maximum attenuation frequency of the cylindrical shell is changed. The maximum attenuation frequency increases as the number of ring ribs increases. The vibration attenuation of the structure under multi-ribbed is higher than the single-ribbed at the middle frequency band, but lower than the single-ribbed at the high frequency band. The multi- ribbed structure can reduce the low-frequency radiated acoustic power of the structure, but it will affect the high-frequency acoustic radiation characteristics of the structure.

Keywords: cylindrical shell, ring rib, Sono-elasticity, vibration attenuation, radiated sound power.

1. Introduction

The ribbed cylindrical shell structure is widely used in underwater vehicles. The existence of the ring ribs strengthens the strength and hinders the propagation of waves in the structure. It will affect the vibration and radiation characteristics of the structure. The ring ribs of shell are seen as vibration isolation masses [1], and the effect of vibration isolation mass on structural vibration characteristics was widely studied. Yu [2] simplified the ship structure into a double-layer plate structure and studied the vibration and isolation effect of the connecting plate on the double-layer plate structure. According to the effect of the ribbed plate on the structure, Qian [3] studied the propagation characteristics of several arranged vibration isolation masses from the propagation characteristics of single vibration isolation mass. Xia [4] analyzed the vibration attenuation function of L-shaped plate based on wave theory. In the paper [5], the plate structure model of the equal-mass hollow beam and solid beam vibration isolation mass were researched. Ji [6] based on the principle of impedance mismatch, the effect of vibration isolation on the vibration and acoustic radiation in the pedestal was studied. The influence of vibration isolation mass on the vibration acceleration of structural model was studied in the paper [7]. Numerical calculation analysis and experimental research prove that the vibration isolation mass has a good effect on suppressing structural acoustic propagation.

At present, the research on the wave resistance effect of the vibration isolation mass is relatively rare, and the research results mainly come from the study of the plate structure. In this paper, based on the thin shell structure theory and three-dimensional acoustic elastic theory, the vibration and radiated acoustic power of the shell are taken as the target, and the acoustic radiation of the ring rib structure to the cylindrical shell is studied. The influence of different ring rib arrangements on the acoustic radiation was analyzed and discussed. The influence of the ring rib structure on the vibration performance of the cylindrical shell structure and its mechanism are summarized.

2. Theoretical calculation of vibration and acoustic radiation

For the cylindrical shell, the column coordinates (r,θ,z) are used for analysis. The coordinate origin is the midpoint of the axis of the cylindrical shell. The corresponding coordinates are (u,v,w). The cylindrical shell has a radius of a and a thickness of h. For the thin shell structure h/a1. The modal expansion method can be used to solve the displacement expansion into a series of numbers as follows:

(1)
u θ , z = m , n U m n c o s n θ c o s k m z , v θ , z = m , n V m n s i n n θ c o s k m z , w ( θ , z ) = m , n W m n c o s n θ s i n k m z ,

where m m=0,1,2, and n n=0,1,2,  are the Modal order, km is the eigenvalue, which can be determined by boundary conditions.

The external force applied to the cylindrical shell structure is f(θ,z). Assume that the ring rib has only normal pressure g(θ,z) on the shell. The force can be expanded into series forms:

(2)
f θ , z = m , n f m n c o s n θ c o s k m z , g θ , z = m , n g m n c o s n θ c o s k m z .

Substitution of Eq. (1) and Eq. (2) into the governing equation gives the vibration equation of the ribbed cylindrical shell, it can be written as follows:

(3)
U ˙ m n Z m n M = f m n - g m n ,

where ZmnM is the mechanical impedance of the cylindrical shell.

Assume that number of ring ribs in the cylindrical shell is T, and the coordinates of the rib in the z direction is zj j=1,2, ,T. The total force of the ring rib is expressed as follows:

(4)
g θ , z = m , n j = 1 T Z n r U ˙ m n c o s n θ c o s k m z j δ z - z j ,
(5)
g m n = Z n r L q = 0 j = 1 T U ˙ q n c o s k q z j c o s k m z j = q = 0 U ˙ q n Z q m n r .

Substitution of Eq. (5) into Eq. (3), Eq. (3) can be written as:

(6)
U ˙ m n Z m n M + q U ˙ q n Z q m n r = f m n .

The modal vibration velocity can be solved by Eq. (6). And so, can the displacement.

The propagation coefficient of a structure can be represented by the vibration between two points. Define the attenuation of the structure acoustic as follows:

(7)
R = 20 l g u 1 u 2 .

In which the vibration displacement of the test point is u2, and the vibration displacement of the reference point is u1.

According to the modal superposition method, the modal response of each order of the structure can be solved, and the radiation wave velocity of each mode is calculated. The acoustic pressure wave acoustic pressure expression in the frequency domain is as follows [8]:

(8)
p = - ρ 0 i ω - U x r = 1 m ϕ r q r ,

where ρ0 is Fluid density, ϕr is the rth mode radiated wave velocity potential, qr is the rth coordinate component.

The radiated acoustic power of the shell is:

(9)
P ω = 1 2 S R e p θ , z u ˙ * θ , z d S .

3. The influence of ring rib on vibration and acoustic radiation of cylindrical shell

This paper focuses on the normal vibration of the structure, taking cylindrical shells with different ribbed forms as analytical models. The cylindrical shell is simple support at both ends. The thickness is 0.01 m. The radius is 1 m. The length is 4 m. The thickness of rib is 0.01 m and the height is 0.1 m. The material of the structure is steel, and so are the ring ribs. A unit force is acted near the left end of the bottom of the structure, observing the vibration response and its attenuation at the position of the excitation position to the symmetrical end. The schematic diagram of the model is shown in Fig. 1.

Fig. 1. Schematic diagram of ribbed cylindrical shell structure

Schematic diagram of ribbed cylindrical shell structure

3.1. The influence of ring rib on vibration of cylindrical shell

In order to research the influence of ring ribs on the vibration of cylindrical shell structure, a non-ribbed cylindrical shell and a single ribbed cylindrical shell were established. Fig. 2 shows the result of the vibration attenuation from the test point to the excitation point.

It can be seen that the vibration attenuation before and after the ribbed is similar at low frequency, and the change is obvious after 200 Hz. When it is not ribbed, the attenuation effect is worse than that of the ribbed cylindrical shell, the vibration attenuation has a negative value around 90 Hz, and the cylindrical shell structure before ribbed has the maximum attenuation at the frequency 230 Hz. After ribbed, the frequency of the maximum attenuation is around 320 Hz. The physical mechanism is that the structure vibration wavelength is longer at low frequency, and the ring rib has less suppression effect on the structure wave; as the frequency increases, the structural vibration wavelength becomes shorter, and the ring rib has a greater suppression effect on the structure wave, and the vibration isolation, the effect is increased.

The vibration velocity level of the structural excitation position and the test position (reference velocity is 10-6 m/s) was analyzed as shown in Fig. 3. It can be seen that the vibration velocity of the excitation position does not change much before and after ribbed, especially when the frequency is below 400 Hz. The vibration velocity of the test position is only changed less than 200 Hz before and after ribbed. The change above 200 Hz is very obvious, which is related to vibration attenuation. The change of the quantity is consistent; the anti-resonance peak appears at the excitation position at 90 Hz, and the anti-resonance peak at the test position appears near 210 Hz. Due to the change of the anti-resonance peak, the extreme frequency of the structural vibration attenuated also changes.

Fig. 2. Vibration attenuation of non-ribbed cylindrical shell and single-ribbed cylindrical shell

 Vibration attenuation of non-ribbed cylindrical shell and single-ribbed cylindrical shell

Fig. 3. Vibration velocity level of non-ribbed cylindrical shell and single- ribbed cylindrical shell

 Vibration velocity level of non-ribbed  cylindrical shell and single- ribbed cylindrical shell

3.2. The influence of multi-ribbed on vibration of cylindrical shell

A multi-ring rib structure model was established to study the effect of multi-ring rib structure on structural vibration. The ribs were applied every 0.4 m in the cylindrical shell. Compared with the vibration response of the single-ribbed cylindrical shell in Section 3.1, the results were shown in Fig. 4. It can be seen that the vibration attenuation of the multi-ribbed and the single ribbed at the low frequency is almost the same. At the middle frequency, the vibration attenuation of the multi-ribbed is significantly higher than that of the single ribbed, while the single ribbed is higher at high frequency. The physical mechanism is that the structure vibration wavelength is longer at low frequency, and the rib has less suppression effect on the structure wave; as the frequency increases, the structural vibration wavelength becomes shorter, and the rib has a greater suppression effect on the structure wave, and the vibration isolation the effect is increased. At the same time, the existence of multi-ring ribs enhances the suppression of structural waves. On the other hand, the increase of ring ribs enhances the stiffness of the structure, which reduces the suppression of high-frequency vibration of the structure. The vibration attenuation of the structure under the cyclic rib is higher in the middle frequency band than in the single ring rib, while the high frequency band is lower than the single ring rib.

The corresponding structural excitation position and the vibration velocity level of the measuring position (reference speed 10-6 m/s) are shown in Fig. 5. Since the multi-ribbed significantly change the characteristics of the structure, the vibration velocity grades of the multi-ribbed structure and the single-ribbed structure are significantly different after 100 Hz. In the calculation frequency band, only two peaks appear in the multi-rib structure, which is obviously due to the presence of multi-ring ribs makes the stiffness of the structure larger.

4. The influence of the distribution of ring rib on the acoustic radiation of cylindrical shell

For the cylindrical shell model researched above, the three-dimensional hydroelastic theory was used to calculate the radiated acoustic power. The calculation result was shown in Fig. 6. It can be seen that at the low frequency, the radiated acoustic power of the non-ribbed cylindrical shell and the single-ribbed cylindrical shell all show peaks, while the multi- ribbed structure does not show peaks at the low frequency, and the third appear obvious near 150 Hz. At the middle frequency, the radiated acoustic power of the non-ribbed structure and the single ribbed structure is not much different, and the radiated acoustic power of the multi- ribbed structure is slightly reduced. At the high frequency band, the radiated acoustic power of the multi-ribbed structure is significantly higher than that of non-ribbed structure and single ribbed structure. The physical mechanism is as follows: the cylindrical shell structure shell is thin, and it is easy to generate low-frequency breathing mode. When the ring rib is applied in the structure, the respiratory mode frequency of the structure becomes larger, but the bending rigidity of the ring rib is not significant. When the number of inner ring ribs in the structure increases to a certain number, the respiratory modal frequency will be higher than the first-order bending mode frequency of the structure. The non-ribbed structure and the single- ribbed structure in the text have obvious peaks at low frequencies, which is due to the low structure. The peak breathing mode is caused, and the peaks appearing at the same time at 150 Hz are caused by the first-order bending mode of the cylindrical shell. Since then, due to the suppression of the ribs, the radiated acoustic power of the multi-ribbed structure in the middle frequency band is slightly lower than that of the non-ribbed structure, but at the same time, due to the strengthening effect of the ribs, the low-order mode of the structure is high-frequency, so that the multi-ribbed structure the radiated acoustic power at high frequencies is higher than that of without ribs.

Fig. 4. Vibration attenuation of single-ribbed cylindrical shell and multi-ribbed cylindrical shell

 Vibration attenuation of single-ribbed cylindrical shell and multi-ribbed cylindrical shell

Fig. 5. Vibration velocity level of single-ribbed cylindrical shell and multi-ribbed cylindrical shell

 Vibration velocity level of single-ribbed cylindrical shell and multi-ribbed cylindrical shell

Fig. 6. Radiated acoustic power level of cylindrical shell structure with different ribbed forms

 Radiated acoustic power level of cylindrical shell structure with different ribbed forms

5. Conclusions

In this paper, the vibration variation of the cylindrical shell before and after the ring rib and after adding multiple ring ribs are compared and analyzed. Summarizing its general laws, and discussing the effects of different ribbed forms on structural acoustic radiation, the main conclusions are as follows.

The influence of the arrangement of the ring ribs on the vibration of the cylindrical shell is mainly reflected at the medium and high frequency and has little effect on the low frequency. The ring ribs changes the maximum attenuation frequency of the cylindrical shell, and as the number of ring ribs increases, the maximum attenuation frequency also increases. The vibration attenuation of the structure under multi-ribbed is higher at the middle frequency than the single ribbed shell, and the high frequency is lower. The multi-ring rib structure can reduce the medium-low frequency radiated acoustic power of the structure, but it will affect the high-frequency acoustic radiation characteristics of the structure.

Acknowledgements

The research leading to these results has received funding from the National Natural Science foundation of China (NSFC) under grant No. 51679245. The support mentioned above is gratefully acknowledged.

References

  1. Cremer L., Heckl M., Ungar E. E. Structure-Borne Sound. Second Edition. Bedim Springer-Verlag, 1988. [Publisher]
  2. Yu H. Transmission reduction of structural vibration by combining blocking mass and damping. Ship Engineering, Vol. 37, 2015, p. 37-39+65. [Search CrossRef]
  3. Qian D. J., Yao X. L., Ji F. Impeding vibration wave propagation from several arranged vibration isolation masses. Applied Acoustics, Vol. 28, Issue 5, 2009, p. 321-329. [Search CrossRef]
  4. Xia Q., Chen Z. Application of L-shaped plates with blocking mass to the vibration isolation of cabin shells. Chinese Journal of Ship Research, 2013. [Search CrossRef]
  5. Wen H. B., Peng Z. L., Liu L. B. Vibration-isolating performance of hollow-square-steel blocking mass based on hybrid FE-SEA method. Journal of Vibration and Shock, Vol. 34, 2015. [Search CrossRef]
  6. Ji F., Yao Yao X. L., Ye X. The influence of blocking mass parameters on the vibration isolation performance of a power cabin. Journal of Marine Science and Application, Vol. 10, 2011, p. 25-32. [Publisher]
  7. Wang X. Z., Sun L. Q., Yao X. L. Isolation characteristics of cylindrical shell with blocking mass bass. Huazhong University of Science and Technology, Vol. 40, 2012, p. 50-53. [Search CrossRef]
  8. Zou M. S. Three-Dimensional Sono-Elasticity of Ships. Wu Xi, China Ship Scientific Research Center, 2014. [Search CrossRef]