Analytical and finite element modeling of pressure vessels for seawater reverse osmosis desalination plants

Evaluation of Optimum Configurations for Composite Oilfield Three-Phase Separator Pressure Vessel

“…The optimum layup winding angle for every lay-up configuration and the corresponding minimum allowable structural wall thickness for investigated filament-wound pressure vessels were related to filament properties. The data obtained from the mathematical solution were broadly consistent with the major trends in reference [19]. However, different filaments were used some lay-ups conducted the same winding angle Due to different filaments used, slight differences in optimum lay-up winding angles regarding neat layups and hybrid lay-ups from those in reference were obtained.…”

“…Parametric models are constructed using finite element modeling. The results are validated using data obtained from mathematical solution introduced in previous work [19] for pure pressure load case and developed solution for operating load case. Parametric models were constructed to determine the effect upon the design safety for both operating and hydro-test load cases.…”

“…The proposed FE model predicted the impact curves precisely comparing with the experimental work undergone in the same work. Kamal et al [19] proposed a mathematical solution and finite element model to identify weight saving can be achieved using composite versus stainless steel pressure vessel under pure pressure only. Four diameter size vessels were used; E-glass/epoxy, carbon/epoxy (AS4/3501-6) and hybrid of both were employed for five layup configurations.…”

“…Previous research has studied mathematically filament wounded pressure vessels subjected to internal pure pressure [19]. In this investigation, a mathematical model based on classical lamination theory, laminates lay-ups, fiber orientation, and layers coordinate notation used in reference [19] was employed for both pure pressure and operating load cases. Two types of unidirectional composite materials are used namely; S-glass/epoxy and carbon/epoxy (IM6/SC1081), their properties are indicated in Table I [22].…”

“…For simplicity the shear force per unit length, N s is implemented in mechanical loading matrix as a ratio of the axial thrust force per unit length, N x due to internal pressure as such that N s / N x =0 to 5 (with a step size of 0.1). The detail of the mathematical model is fully described in previous work [19] ; therefore, major changes are only outlined here. The current mathematical model in use is valid only for plane stress load case so, hydro-test load case could not be simulated using such model.…”