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Mathematical Modelling of Longitudinal Vibration on Propulsion System 5200 DWT General Cargo Ship Benedicta Dian Alfanda; Adi Wirawan Husodo; Intan Rahmahwati; Febry Yulistiawan
International Journal of Marine Engineering Innovation and Research Vol. 10 No. 1 (2025)
Publisher : Department of Marine Engineering, Institut Teknologi Sepuluh Nopember

Show Abstract | Download Original | Original Source | Check in Google Scholar | DOI: 10.12962/j25481479.v10i1.4763

Abstract

The vibration level of the propulsion system will change during its operation. This vibration is caused by harmonic excitation forces produced by the rotation of the main engine and propeller shaft. Ship propulsion systems experience longitudinal, torsional and lateral vibrations. Excessive vibration will produce noise and reduce engine performance. Vibrations can also cause resonance in the system, which can be fatal and damage the structure. The excitation frequency value is close to or equal to the natural system frequency, which causes resonance. This paper has identified the vibration response of the propulsion system by using numerical software through mathematical modelling governed by ABS. In addition, the total vibration response was obtained using the modal analysis method by summing up the contributions of each mode. The excitation source generated is due to the rotation of the main engine. Ultimately, the response obtained will be adjusted to the standard class. The modelling results obtained a 3-Degree-of-Freedom forced vibration model consisting of three masses and three springs. The resulting response values are displacement and velocity, where the highest response occurs at 347 rpm with a deviation of ±0.1345 mm to ±0.3371 mm and a velocity value of ±4.8847 mm/s to ±12.2424 mm/s. The slightest response occurs at 459 rpm with a deviation range of ±0.0034 mm to ±0.0050 mm and velocity values of ±0.1634 mm/s to ±0.2382 mm/s. Based on all the results of adjusting the vibration response value with the ABS class vibration limit graph, the vibration is still below the permissible threshold line.
Application Of the Finite Element Method for Evaluating the Stress Due To Operating Load In High Energy Piping System Pekik Mahardhika; Adi Wirawan Husodo; Ekky Nur Budiyanto; Benedita Dian Alfanda; Rina Sandora
International Journal of Marine Engineering Innovation and Research Vol. 10 No. 2 (2025)
Publisher : Department of Marine Engineering, Institut Teknologi Sepuluh Nopember

Show Abstract | Download Original | Original Source | Check in Google Scholar | DOI: 10.12962/j25481479.v10i2.6379

Abstract

The stress value of the piping system will change during operating conditions. The stress value affects the integrity of the piping system. Excessive stress will cause deformation and damage to the piping system. The operating condition parameters of the piping system are temperature and pressure. The High-Energy Piping (HEP) system is subjected to high pressures and temperatures, which can cause significant stresses on the piping components. So stress analysis needs to be carried out to ensure that the piping system has strength and flexibility. The Cold Reheat Pipe (CRP) steam line is one of the High-Energy Piping Systems in this steam power plant. CRP consists of CRP BS 130 and CRP BS 131. This paper is about evaluating the stress due to operating loads in 2024 (temperature, pressure, and remaining thickness) for steam lines on the high-energy piping system using the finite element method and refers to ASME B31.1. The output stress values in the piping system in this paper consist of stress due to sustained load, stress due to thermal load, and hoop stress. The CRP BS 130 modeling results show the maximum stress due to sustained load (166.6 kg/cm2), the maximum stress due to the thermal load (112.8 kg/cm2), and the maximum hoop stress (855.6 kg/cm2). The CRP BS 131 modeling results show the maximum stress due to sustained load (974.2 kg/cm2), the maximum stress due to the thermal load (123.5 kg/cm2), and the maximum hoop stress (938.9 kg/cm2). The results of the stress evaluation due to the operating load were still below the allowable stress and are still permitted by the ASME B31.1 Code.