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ASME PCC-1 DOWNLOAD

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The Bolted Flange Joint Assembly (BFJA) from ASME is a unique collection and the guidelines described in this document apply to pressure-boundary flanged. I am after a copy of ASME PCC-1 2013. Does anyone have this to share?. ASME PCC-1, Guidelines for Pressure Boundary Bolted Flange Joint Assembly ( BFJA), is a standard created and published by the American Society of.


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Pressure Boundary. Bolted Flange Joint. Assembly. A N A M E R I C A N N AT I O N A L S TA N D A R D. ASME PCC-1–2010. (Revision of ASME PCC-1–2000) . Assembly Bolt Torque for SA-105 Steel Weldneck Assembly Bolt Torque for SA-105 Steel Weldneck Flanges, Flanges, SA-193 B7 Steel Bolts, and Spiral-Wound Gasket SA-193 B7 Steel Bolts, and Spiral-Wound Gasket With. ASME PCC-1-2013 Table for Pressure Boundary Bolted Flange Joint. PCC-1-2013 - Download as PDF File .pdf) or read online. ASME.

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The design works was divided into two major parts namely: Transmission system design, and water storage facility Design. The offered Overhead Water Tank is manufactured at the vendor's end using the fine gr The tanks may be covered on top.

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ASME PCC-1-2000- Guideline f Pressure Boundary Bolted Flange.pdf

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Pcc-1 download asme

Septic Tank, Manhole and Dispersion Trench 15 40 7. Low Speed Mixer - 1,200 Gallon Tank. Blocks help you save time, maintain consistency, and reduce file size by reusing and sharing content rather than re-drawing it every time you need it. The R. Any fastener with thread dimensions less than the minimum major diameter or the minimum pitch diameter should be replaced. Appendix N provides supplementary information on the bolt reuse topic. Coatings over approximately 0. Roughness, gouges, and protrusions should be removed from these surfaces.

On severely damaged flanges, machining this area may be required, in which case the minimum acceptable residual flange thickness must be considered. The use of throughhardened, flat washers4 may be appropriate to provide smooth and square nut-bearing surfaces.

It results in maximum sealing surface contact, maximum opportunity for uniform and design-level gasket loading, and reduced friction between the nut and the flange. Guidelines for aligning flanged joints are provided in Appendix E. However, it is generally recognized that the use of through-hardened steel washers will improve the translation of torque input into consistent bolt stretch.

See Appendix M for a suitable through-hardened washer specification guideline. These are important considerations when torquing methods either manual or hydraulic are used for bolt tightening. Flat washers also promote improved load distribution.

See Appendix M for a suitable through-hardened washer purchase specification guideline. The torques were adjusted based on industry experience and verified by bolt elongation measurements. See Appendix K for equivalent nut factor. For second and subsequent tightening by torquing methods, use of lubricants and torque values as specified for noncoated bolts is recommended. See section 12 Target Torque Determination. The root areas are based on coarse-thread series for sizes M27 and smaller, and 3-mm pitch thread series for sizes M30 and larger.

The basis for the torque values in Table 1M are described in the Notes below. When conditions vary, such as different bolt materials or different coatings, from those considered in this table, refer to Appendix K, or optionally to Appendix J, of these guidelines to compute appropriate torque values. Customary Units See section 12 for instructions on how to adjust torque values in this table. Target Torque, ft-lb Nominal Bolt Size, in. The root areas are based on coarse-thread series for sizes 1 in.

The basis for the torque values in Table 1 are described in the Notes below. The Target Torque values were computed using nut factors selected to achieve a Target Prestress of 50 ksi.

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Reuse of a gasket is not recommended. However, the substrates of grooved metal gaskets with facing layers may be reused after having been reconditioned and refaced in a manner consistent with the original product specification. The reinstallation of gaskets so refurbished is not considered gasket reuse since the sealing performance of the gasket has been restored. For other gasket types, experience has clearly shown that only a new gasket will reliably provide the necessary plastic deformation and elastic recovery characteristics essential to achieve an effective seal.

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Visual or physical inspection of a used gasket for apparent damage is not sufficient to detect such sealing surface factors as work-hardening, brittleness, or the effects of heat or interaction with the service fluid. No portion of the gasket should project into the flow path.

Particular care should be taken to avoid adhesive chemistry that is incompatible with the process fluid or could result in stress corrosion cracking or pitting of the flange surfaces.

Do not use tape strips radially across the gasket to hold it in position.

Do not use grease. Lubrication should be applied irrespective of the tightening method used. On the second and subsequent tightening operations, apply lubricant as described in d. When reusing coated bolts or if lubricant is applied to new or reused coated bolts, the Nut Factor will change and therefore the torque values should be adjusted accordingly refer to Appendix K.

Particular care should be taken to avoid lubricant chemistry that could contribute to stress corrosion cracking, galvanic corrosion, oxygen auto-ignition, etc. If nuts do not hand tighten, check for cause and make necessary corrections.

For the purposes of joint assembly, the Table 4 and Table 4.

ASME PCC-1:2013

Risk-based methods have been employed on bolted joints to date, but typically methods used have been limited to qualitative probability assessment approaches, which all tend to be reactive in nature, rather than proactive.

For example, this might include identifying all high-temperature heat exchangers as being at risk of leakage, or keeping a leakage log and establishing a corresponding list of "bad actors" for a given site. In some cases, it is historically clear that certain joints will be problematic, for example ASME B16. However, these approaches are limited in that they are reactive and qualitative. A history of leakage must be established and joints assessed against that list.

This is obviously not ideal as it requires, in the first place, sufficient leakage to have occurred so as to establish a base-line and, secondly, as a qualitative method it cannot be adapted to new configurations nor can it account for variation in practices from one site to another. The RBJI approach looks at the probability of a joint leaking based on the cumulative risk of all of the possible damage mechanisms for the joint.

The first step in defining the methodology was to identify the most appropriate damage mechanisms for joint leakage. At present these have been identified based on the most common mechanisms that have historically been found to causejoint leakage: a Residual probability of failure for the site RPOF This is the residual risk associated with flange leakage at the site due to flange assembly practices.

It is essentially the risk associated with the probability of incorrect assembly of the joint. The risk increases with poorer assembly practices and reduces as the assembly practices assembler qualification, procedures, load control, etc. The probability of leakage is determined based on the buffer against leakage in the joint integrity diagram as outlined in WRC 538 [2]. In the case of the bolts it is bolt yield, for the flanges it is the limit of gross plastic deformation in accordance with WRC 538 [2] and for the gasket it is the stress that will cause irrecoverable damage.

In all cases, this damage mechanism must be assessed for both the assembly and operating cases. The probability of failure is obtained by comparing the calculated operational rotation during transient and upset conditions with an acceptance limit based on the gasket type employed.

Once again, the calculated flange rotation is compared to an acceptance limit based on the gasket type employed. The differential radial expansion is calculated for the worst-case, which typically occurs during thermal transients. The acceptance limit is based on the gasket type employed. The relatively short term relaxation of the gasket is included in the calculation performed for POFlb- h Joint alignment probability of failure POFal This is the probability of joint misalignment contributing to joint leakage and is based on the force required to bring piping into alignment.

It is not typically relevant for equipment and is different to piping external loads, which are included in POFlb. Depending on the application, it may be easier or more appropriate to list the Failure Period FP associated with the joint or damage mechanism. The FP is simply the inverse of the POF and is therefore the number of years expected between leakage that is calculated for the joint or damage mechanism.

The calculation methodology for each of the damage mechanisms is based on joint integrity calculation methods and experience with limits associated with those calculations which has been gained over the last 10 to 15 years.

For each damage mechanism it is necessary to firstly calculate the characteristic measure for the joint being considered and then, secondly, to compare that measure to a relationship between the measure and the likelihood of leakage.

The RBJI method can be applied to demonstrate the impact of proposed improvements for any given joint.

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The use of RBJI is particularly applicable when it becomes necessary to provide justification for heat exchanger or piping replacement in cases where the existing joints are known to be problematic.