FlangeTorque
Flange Integrity Management Platform · v3.0
1

Flange & Bolt Data

ASME B16.5 / B16.47
2

Bolting

Yield/UTS shown are room-temperature values from the material database. For elevated design temperature, derate using the applicable ASME allowable-stress tables before relying on the result.
3

Gasket & Required Loads

ASME VIII App. 2 (m, y)
Wm1 = π · b · G · y  |  Wm2 = (π/4) · G² · P + 2π · b · G · m · P  |  Required = max(Wm1, Wm2)
Effective gasket width b and reaction diameter G follow the ASME Appendix 2 facing-sketch rules (b = b0 if b0 ≤ 6.35 mm, otherwise b = 2.52√b0, G = OD − 2b). m and y are suggested values - confirm with the gasket manufacturer.
7-9

Target Stress, Torque & Bolt Verification

Target stress = preload% × derated yield  |  F = stress × At  |  T = K · F · D
PCC-1

Actual tightening passes

apply in the star order
9

Bolt stress check

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10

Hydraulic Tensioning

Jack load = F × load factor ÷ efficiency  |  Hydraulic pressure = Jack load ÷ piston area
11

Tightening Sequence

cross / star pattern
Multi-pass per ASME PCC-1: Pass 1 hand-tight/snug, Pass 2 ~30%, Pass 3 ~60%, Pass 4 ~100% in the cross/star order shown, then a final clockwise (circumferential) pass at 100% to pick up relaxation.
12

Recommended tool

13-16

Turnaround Labor, Cost & Criticality

16

Critical joint classification

15

Flange-Face Repair: Geometry, Volume & Deposition

Volume × density = deposited weight  |  Arc time = weight ÷ deposition rate
17

Engineering Reports & Export

All reports are generated in your browser - nothing is uploaded. Reports carry the AIEnginear branding, tag, engineer, revision and timestamp.
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i

Bolt Torque & Flange Joint Guide

This guide explains how FlangeTorque turns a flange and gasket into a defensible bolt-up plan, using the ASME VIII Appendix 2 load method with ASME PCC-1 assembly guidance.

How flange bolt torque is calculated

The chain is: find the load the joint needs, convert that into a bolt preload, then convert preload into a torque. The required load is the larger of the gasket seating load (Wm1) and the operating load (Wm2). The target preload comes from a chosen bolt stress, typically 40 to 75 percent of yield per PCC-1, and torque follows from T = K x F x D.

Gasket seating and operating loads

Wm1 = pi x b x G x y seats the gasket, where b is the effective seating width, G the gasket reaction diameter and y the seating stress. Wm2 = (pi/4) x G squared x P + 2 x pi x b x G x m x P keeps the joint sealed in service, combining the hydrostatic end force with the gasket compression needed under pressure P, where m is the gasket maintenance factor.

The nut factor and torque scatter

The nut factor K wraps all the friction in the threads and under the nut into one number. Because friction varies, a single torque value really represents a window, often plus or minus 20 to 30 percent of achieved preload. That scatter is why critical joints are frequently hydraulically tensioned, which applies load directly and far more repeatably.

Tightening sequence

Bolts are tightened in a cross or star pattern over several passes so the gasket compresses evenly. A common scheme is a snug pass, then roughly 30, 60 and 100 percent of target in the star order, finishing with a clockwise pass to recover relaxation. FlangeTorque draws the exact numbered order for your bolt count.

Turnaround planning and flange repair

For a shutdown, multiply bolts and flanges by realistic make-and-break times to get crew hours, then cost them out. Where a flange face is damaged, the repair module estimates weld-overlay volume, deposited weight, arc time and cost so the repair can be planned alongside the bolt-up.

Standards

Methodology follows ASME PCC-1 (assembly), ASME VIII Div.1 Appendix 2 (load method), ASME B16.5 / B16.47 (flanges), ASME B31.3 (piping), with reference to EN 1591-1, API 570 / 574 / 571 and ISO 898 / ASTM bolt material standards. FlangeTorque is a screening and planning aid; confirm against the governing code, gasket data and a qualified PCC-1 procedure before live work.

8

Flange Integrity Analysis

derating · relaxation · thermal · leakage
T

Temperature derating

R

Preload relaxation & creep

dT

Thermal expansion

dL

Bolt elongation / ultrasonic target

!

Leakage risk assessment

EN

EN 1591-1 seating reference

Simplified EN 1591-1 reference check (gasket surface pressure vs Qmin / Qsmax). It is not the full iterative EN 1591-1 calculation - use certified software for code compliance.
%

Tightening method preload accuracy

Preload scatter is method-dependent. Achieved preload ranges below assume the same target; tensioning and ultrasonic give the tightest control.
R

Reliability, Yield Margin & Advisor

nut-factor scatter simulation
MC

Bolt-load scatter simulation

4000 trials
Y

Yield margin analysis

O

Joint categorization (Appendix O)

F

Face condition

A

Engineering advisor

rule-based recommendations
Recommendations are generated by a deterministic rule set from the current inputs - not a generative model. Use engineering judgement and the governing code.
9

Joint Register & Flange Tracking

stored locally
TagSize/ClassGasketTorqueStatusCriticalInspected
HT

Hydrotest readiness

Test pressure factor is applied to design pressure (B31.3 hydrostatic = 1.5x design by default). Confirm the test pressure, temperature correction and joint status before pressurising.
API

API 570 inspection

API 570 sets piping inspection intervals by service class; the register flags critical joints for shorter intervals. This is a planning aid - follow your inspection program and RBI assessment.

Live results -

Governing load (Wm)-
Required / bolt-
Target preload / bolt-
Target torque-
Torque window-
Bolt stress (% yield)-
Bolt utilisation-
FlangeTorque provides screening-grade results for planning. Confirm bolt stress, gasket selection and torque against the governing code, gasket manufacturer data and a qualified ASME PCC-1 assembly procedure before live work.
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Screening-grade engineering aid · not a substitute for a qualified PCC-1 procedure