Maximum Flex Or Ball Joint Angle Drilling Riser

RP 16Q: Design, Selection, Operation, and Maintenance of Marine Drilling Riser Systems ing. In cases of extended drilling on a harsh environment location, such as on a North Sea template, a fatigue analysis of the riser may be advisable. The mean and maximum flex/ball joint angle limits given for the normal drilling mode are intended to prevent wear and keyseating damage to the riser and flex/ball joint. Prudent operational procedure should strive to maintain these angles as small as possible, and consider 2.0 degrees (mean) and 4.0 degrees (maximum) as upper bounds. The maximum flex/ball joint angle limits for the connected nondrilling mode and disconnected mode are intended to prevent damage to the riser, flex/ball joint, and BOP stack. The upper flex/ball joint angle rarely has a significant effect on riser design; however, this angle should be considered when evaluating clearances in the moonpool area.

The purpose of the maximum stress analysis is to ensure that the riser is strong enough to support the maximum design loads. This is accomplished by requiring the riser to support the maximum design loads while keeping the maximum stresses below the allowable stress. This limit is intended to prevent structural deformation that could lead to failure and includes a margin of safety. All stresses in Table 3.1 refer to the von Mises stress criterion (see Higdon, et al (1976)). Local peak stresses (see Glossary, Appendix A) are not considered for the maximum load analysis; however, these peak stresses could be of concern for evaluating the fatigue fife of the riser. Fatigue analysis is discussed in Appendix C, Section C.2.

A minimum tension setting is required to ensure the stability of the riser. The tension setting should be sufficiently high so that the effective tension, as addressed in Section 3.4.3, is always positive in all parts of the riser even if a tensioner should fail. In most cases the minimum effective tension is encountered at the bottom of the riser.

The minimum top tension, T^, is determined by:

min SRmin f where,

TSRmin = Minimum Slip Ring Tension = W f . - B f, + A.[d H - d H ]

awt nbt i mm ww and

WB = Submerged Riser Weight above the point of consideration fwt = Submerged Weight Tolerance Factor (minimum value = 1.05 unless accurately weighed)

Bn = Net Lift of Buoyancy Material above the point of consideration fbt = Buoyancy Loss and Tolerance Factor resulting from elastic compression, long term water absorption, and manufacturing tolerance. (Maximum value = 0.96 unless accurately known by submerged weighing under compression at rated depth)

Aj = Internal Cross Sectional Area of Riser including choke, kill, and auxiliary fluid lines d = Drilling Fluid Weight Density

Hm = Drilling Fluid Column to point of consideration dw = Sea Water Weight Density

Hw = Sea Water Column to point of consideration including storm surge and tide

N = Number of Tensioners Supporting the Riser n = Number of Tensioners Subject to Sudden Failure

Rf = Reduction Factor Relating Vertical Tension at the Slip Ring to Tensioner Setting to account for fleet angle and mechanical efficiency (usually 0.9 - 0.95)

Note that in the above equation for TSRmjii, the exterior pressure, dwHw, is multiplied by the internal cross sectional area of the riser, A., rather than the exterior cross sectional area, A. This is because the buoyancy of the riser pipe walls, dwHw (Ao - A_), has been included in the submerged riser weight, Ws.

See Sample Calculation D.2 in Appendix D for a determination of minimum tension setting.

The significant dynamic stress range limit should also be used in conjunction with the maximum load analysis. This limit is intended to provide some control on the fatigue damage accumulated by the riser. Incorporation of this limit in the maximum load analysis eliminates large dynamic stresses which can lead to accelerated fatigue.

Additional operating modes which might influence design should be considered. Specifically, the disconnected mode, handling tool interfaces, hang-off on either spider or riser hang-off structure, special handling situations, and emergency conditions should be reviewed for their impact on riser system design.

The load and resistance factor design (LRFD) procedure, based on reliability rather than working stress, is rapidly gaining acceptance. This approach is described in Appendix C, Section C.3.

  1. 3.3 Riser Operating Manual. Results of the design analysis should be appended to the riser operating manual (See Section 4.2). Instructions for determining required top tensions as a function of all the relevant parameters should be included. The operating tensions provided to the operating personnel should be the tensions which are to be set on the tensioner units. These tensions are to include corrections for tensioner line fleet angles and losses through the tensioner system. Sufficient tension should be set so as to prevent riser buckling in the event of a tensioner unit failure.
  2. 4 RISER ANALYSIS. The mathematical models and the solution techniques which can be used to analyze a drilling riser constitute a highly technical and specialized subject which has been widely treated in the literature. A bibliography is provided for the reader desiring detailed information, and the following text is limited to a general discussion of the pertinent aspects of riser analysis. In particular, reference is made to the API Bulletin 16J, "Comparison of Marine Drilling Riser Analyses."
  3. 4.1 The Use of Riser Analysis. As a general rule, riser analysis has two distinct and different functions.
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