OS-C501
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Offshore Standard DNV-<strong>OS</strong>-<strong>C501</strong>, November 2013<br />
Sec.9 Structural analysis – Page 152<br />
6.1.5 In vibration analysis one may use a coarse structural model if only the first few 'eigenvalues' are of<br />
interest, see [6.2.2]. Nevertheless, a reasonable representation of structural mass and stiffness is crucial.<br />
6.1.6 If a large number of 'eigenfrequencies' are required, one shall apply a detailed description of the structure.<br />
6.1.7 Due account should be taken of fluid-structure interaction effects where these are significant. These may<br />
include resonance between structural response and wave excitation frequencies, or more complex, highfrequency<br />
vibration phenomena (ringing and springing) caused by non-linear wave loads. In some cases of<br />
fluid-structure interaction it may be necessary to perform a dynamic analysis of the coupled fluid-structure<br />
system.<br />
6.1.8 In case of accidental loads, such as explosions, dynamic effects should be considered carefully.<br />
6.1.9 The dependence of the material properties on strain rate should be taken into account, see Sec.4 [3.10].<br />
Guidance note:<br />
Although static material properties may yield conservative predictions of displacements, a strength assessment based<br />
on static properties is not necessarily conservative since both the material strength and the material stiffness may be<br />
enhanced at high strain rates. The higher stiffness may increase the induced stress so that the benefit of the increase<br />
in the material strength may be lost. Furthermore, ductile materials often become brittle at high rates. Thus, the extra<br />
margin provided by ductile behaviour may be destroyed.<br />
There is a lack of sophisticated material models taking the rate dependent behaviour into consideration.<br />
6.2 Dynamics and finite element analysis<br />
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6.2.1 For analysis including dynamic loads with frequencies of interest up to ω cr. , the mesh shall be able to<br />
accurately represent modes associated with frequencies up to 3ω cr. , and a mode superposition analysis shall<br />
include frequencies up to about 3ω cr. .<br />
6.2.2 For 'eigenvalue' analysis, there should be 4 or more times as many degrees of freedom as 'eigenvalues'<br />
to be calculated.<br />
6.2.3 For direct integration methods, the following points should be ensured:<br />
— the time step Dt should be approximately 0.3/ω cr. or less, and should provide numerical stability if the<br />
integration method is conditionally stable<br />
— there should be a match between the type of algorithm and the mass matrix<br />
— abrupt changes in element size should be avoided, thereby avoiding spurious wave reflection and numerical<br />
noise.<br />
7 Impact response<br />
7.1 Testing<br />
7.1.1 Impact test requirements shall be defined since there are no well-established calculation methods today.<br />
7.1.2 Component testing (see Sec.10) should be carried out in order to evaluate the impact characteristics of<br />
the structure/component.<br />
8 Thermal stresses<br />
8.1 General<br />
8.1.1 Changes in temperature from the environment resulting in dimensional changes of the body shall be<br />
taken in account. The general thermal strains, e i , can be expressed as:<br />
e = α ∆T<br />
where α i is the thermal expansion coefficients. Temperature is denoted by T.<br />
i<br />
8.1.2 Residual strains shall be calculated against the reference temperature for which α i was determined. It is<br />
usually the curing temperature.<br />
8.1.3 Accordingly, the stress-strain relations shall be modified to account for the stress free environmentally<br />
induced expansion strains as follows:<br />
{ ε}<br />
= [ S ]{ σ } + { e}<br />
i<br />
DET NORSKE VERITAS AS