In order to facilitate the analysis and calculation of the spring hanger, according to the principle of independence of mechanics, the pipeline stress is divided into two kinds, respectively, by the pipeline pressure, self-weight and other sustained external load generated by the sum of stress Primary stress) and the range of thermal expansion (called secondary stress) due to thermal expansion, cold shrinkage, and other displacements. Spring load hanger pipe in the working state, by the internal pressure, self-weight and other continuous load generated by a stress, shall not be greater than the calculated temperature of the steel under the basic allowable stress. P - design pressure, MPa; Do - pipe diameter, mm; Di - - pipe diameter, mm; MA - self-weight and other continuous external load in the pipe cross-section of the synthetic torque, N · mm; W - pipe section bending moment, mm3; [σ] t - steel at the design temperature The allowable stress, MPa; i - the stress increase coefficient; бL - the sum of the axial stresses due to the internal pressure, the dead weight and other continuous external loads, MPa. The range of thermal expansion stress generated by the thermal expansion / condensation and other displacements of the pipe must satisfy the following formula: σE = iMC / W ≤ f [1.2 [σ] 20 + 0.2 [σ] t + ([σ] t- (2) where [σ] 20 - allowable stress at 20 ° C for pipe steel, MPa; MC - calculated based on full compensation value and elastic modulus at 20 ° C Of the synthetic torque range, N · mm; σE - thermal expansion stress range, MPa; f - stress range of the reduction factor. It is expected that the coefficient f will be related to the number of permutations N of the full temperature of the pipeline during the operating period. F = 1 when N ≤ 2500, f = 4.78N-0.2 when N> 2500.

The structure and model of spring hanger
The Deficiency of Three Kinds of Calculation Methods for Hanger Spacing of Pipeline