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. 2020 Dec 20;13(24):5818.
doi: 10.3390/ma13245818.

The Friction-Induced Vibration of Water-Lubricated Rubber Bearings during the Shutdown Process

Guangwu Zhou  1 , Peng Li  1 , Daxin Liao  1 , Yuhao Zhang  1 , Ping Zhong  2
Affiliations

The Friction-Induced Vibration of Water-Lubricated Rubber Bearings during the Shutdown Process

Guangwu Zhou et al. Materials (Basel). .

Abstract

The vibration noise generated by water-lubricated rubber bearings (WLRBs) seriously reduces the concealment of a ship's navigation. The purpose of this study was to obtain the relationships between friction-induced vibration and the friction coefficient, specific pressure, temperature, and stiffness of the bearing support during the shutdown process of WLRBs. Using transient dynamic analysis (Abaqus/Standard), the shutdown process of the bearing system was simulated by setting a friction coefficient curve, and with the fast Fourier transform (FFT), the data in the time domain were then converted to the frequency domain. In addition, an orthogonal table was applied to select the best level for each factor. The results show that proportionally increasing the friction coefficient and specific pressure caused higher vibrations, and the effect of the specific pressure on vibration is more prominent than that of the friction coefficient. Higher temperatures led to an increase in the peak frequency of noise (squeal) and the virtual value of acceleration. Increasing the stiffness of the bearing support decreased the higher-frequency squeal but dramatically increased the lower-frequency chatter. The results of the study are of guiding significance for the improvement of research methods and the optimization of the materials and structures of WLRBs.

Keywords: friction-induced vibration; shutdown process; transient dynamics; tribology; water-lubricated rubber bearings.

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Conflict of interest statement

The authors declare no conflict of interest.

Figures

Figure 1
Figure 1
Marine propulsion shafting and stern bearing.
Figure 2
Figure 2
Geometric structure of the water-lubricated bearing.
Figure 3
Figure 3
The model of the bearing system and the observation point (N-502).
Figure 4
Figure 4
The curves relating the time, speed, and friction coefficient.
Figure 5
Figure 5
Displacement and frequency spectrum of N-502 with different friction coefficients.
Figure 6
Figure 6
The peak frequency and root mean square (RMS) in the x-direction with different friction coefficients.
Figure 7
Figure 7
Displacement and frequency spectrum of N-502 under different specific pressures with the μ1 friction coefficient.
Figure 8
Figure 8
The peak frequency and RMS in the x-direction under different specific pressures with the μ1 friction coefficient.
Figure 9
Figure 9
Displacement and frequency spectrum of N-502 under different temperatures with the μ1 friction coefficient.
Figure 10
Figure 10
The peak frequency and RMS in the x-direction under different temperatures with the μ1 friction coefficient.
Figure 11
Figure 11
Vibration acceleration displacement and frequency spectrum of N-502 under different stiffness values of bearing support with the μ3 friction coefficient.
Figure 12
Figure 12
The peak frequency and RMS in x-direction under different stiffness values with the μ3 friction coefficient.
See this image and copyright information in PMC

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