By S.S. Rahman and G.V. Chilingarian (Eds.)
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Extra resources for Casing Design Theory and Practice
Solution: From Eq. 5, the cross-sectional area under the last perfect thread, A j p , is" Ajp = - ~ [ ( 9 . 434sq. in. (i) From Eq. 3 one can calculate fracture force as: F~j - 0 . 434x l0 s = 1 , 0 8 6 x 1031bf 31 (ii) Similarly Eq. 625) 905 X 1031bf = From tile above analysis the limiting factor is the joint pullout, so for API Round thread (long), N-80, 9-~ in. casing, the joint strength is" F~j - 9 0 5 x 10:3 lbf. 8) where" Asp Asc - As - area of steel in pipe body, in. 2 area of steel in coupling, in.
Occiirs I x t wreii flanks a n d lwtween t Ilr, crests and roots as a result of: 1)ressurc’ duv t o thread intrrfmwce created 1 ) ~ 19 makeup torque, pressure due to the radial component of the stress created by internal pressure and pressure due to the torque created by the negative flank angle (Fig. 8). Shoulder sealing occurs as a result of pressure from thread interference, which is directly related to the torque imparted during the joint makeup. Low makeup torque may provide insufficient bearing pressure, whereas high makeup torque can plastically deform tlle sealing surface (Fig.
Note that in the second case the additional stress due to bending is more than double that calculated assuming uniform contact with the borehole. In this example both methods produce maximal axial stresses well below the 80,000 psi minimal yield stress of N-80 grade casing. (iii) The minimal ultimate yield strength of N-80 grade casing is c%p psi, so using Eq. 95 x 100,000- = 94,993 psi - 100,000 (160~6-0(}- 801b0~ ~ Inasmuch as Fab/Ajp > 80,000, the above value for joint strength is valid and there is no need to apply Eq.
Casing Design Theory and Practice by S.S. Rahman and G.V. Chilingarian (Eds.)