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See section F-2 of Appendix F for comments on accepting flange joint assembly procedures not currently listed in these guidelines. Avoid using carbon steel brushes on stainless steel flanges. The exception based on experience is flexible graphite that may remain in the surface finish grooves when either a flexible graphite clad or a spiral-wound gasket with flexible graphite filler is to be used as the replacement gasket.

Indications running radially across the facing are of particular concern. Refer to Appendix D for guidelines covering recommended limits on gasket contact surface imperfections and their locations. Appendix C provides recommended final surface finishes.

Qualification of the selected joint assembly procedure may be appro- priate for critical applications. Appendix A provides some notes on qualifying flanged joint assemblers. Appendix B provides a recommended flanged joint assembly procedure qualification test. Indications running radially across the facing are of particular concern. Report any questionable imperfections for appropriate disposition.

Report any questionable results. Appendix D provides a recommendation for flatness tolerance. There fore, other techniques such as turn-of-nut oF tensioning are preferred. Live tightening. Itis typically performed while the unitis online but may also be performed prior to operation using, heating pads toring the flange up to temperature, Since this activity will only inerease the load on the gasket, the risk of leakage is significantly lower than for other activities such as hot bolting furr-of nut: tightening all bolts on a joint while the unit is in operation or during a turnaround, without disas- sembling the joint.

Turn-of-nut is used either to proac- tively increase the gasket stress to prevent leakage in high-temperature or eyelic services or to reseal a small, stable leak. However since the load on the gasket will only increase, the risk of leakage is significantly lower than for other activities such as hot bolting.

Turn-of-mut does not require know! An engineering and risk analysis of the turn-of-nut operation should be carried out to establish that the operation can be performed safely. Generally speaking, itis not appropriate to classify gas- kets as hard or solt based solely on physical harciness or softness of the gasket material itself. For example, 1.

See also hard-faed gaskets. It may not be acceptable 19 categorize by gasket type as extremely thn gaskets of gaskets without sufficient filler will ot il imperfections and therefore are categorized as hard-faced gaskets. Metal-iaced gaskets, such as flat metal, RT, or double- jacketed gaskets, are categorized as hard-faced gaskets. See also hard gaskets. Softfaced gos- ets have suicient sot filler uchas graphite, rubber,or PTFE that both the gasket substrate and flange seating surface finish willbe filled and additional filer exists Gn the gasket such that any small imperfections will also be filled as the gasket is compressed between the flanges.

Sot cat sheet hicks 1. Soft gaskets see Appendix B are more tolerant of ange flatness imperiectionsbut are typically more dlf- cal to assemble. Hard gaskets see Appendix B have Jess compression than soft gaskets and, while this can help with improved assembly duet less bolt interaction crosstalk , it generally means that hard gaskets ate more sensitive to flange flatness outof-toerance.

Its suggested that load-compression test results forthe ase ket being used be obtained fom the gasket manufac to determine which of the listed flatness tolerance limits should be employed Ttis acceptable to gauge mating flanges that have only cone possible alignment configuration and determine that any waviness of the flange faces fs complimentary, such that the seating sufaces follow the same pattern This is found in multipass exchanger joints and s often caused by thermal distortion.

Care should be taken to ensure the correct tolerances are employed for the gasket being installed. Itis important to note that the tolerances apply to the gasket seating surface area where the gasket seats both initially and finally after assembly , D The flange flatness and groove dimensions are examined prior to joint disassembly by inspection of the gap between the outer edges of the raised faces. If the gap at any location around the joint circumference is less than 1.

This eliminates the risk ofthe flange faces, touching during assembly, which can lead to joint leak- age. Once the joint is disassembled, the gasket seating, surface see Fig.

Pass 8 onward: Tighten in circular Passes unt the nuts do not turn. For soft gaskets a minimum of two pattern Passes is required For hard gaskets! This method has been successfully applied in limited applications utilizing harder gaskets in joint configurations commonly found in refining applications, and has been qualified in experimental evaluations a suitable for spiral-wound and fiber-sheet sasket types?

Tightening Sequence for Pattern 3 is described in through 2 below, An example is provided in Fig. F A stepsby-step example is shown in Fig. One tool per every four to eight bolts in the flange should be weed in even-numbered groups of tools equally distributed around the Range. Group Numbering. F-5, with four tools being used fo tighten. All bolts are now numbered in geoups at 90 deg from each of their own number. It is not necessary to do the remaining bolts because the purpose of ths initial Pass is to seat the gasket and square up the flange.

Flange alignment and gap should be checked. The remaining, bolts will have loosened so time can be saved at this point by snugging them again. This is the check Pass that compensates for clastic interaction and brings all bolts into parity. F F There are, generally, two viable options for accepting bolted joint assembly procedures that are not listed in these guidelines, a Option 1 is to use it and learn if it works by experience. Another possibility to implement this option is to use a bolting contractor’s experience or other facility’s experience to prove the method works this, often means relying on secondhand information.

In addition, they are sensitive to flange misalignment either prior to or during joint assembly. F of F, Significant advantage reduction in the number of pas- se is possible by using multiple tightening heads two, four, or more to simultaneously tighten bolts on the joint.

In accordance with para. P Monitor and advise user’s maintenance personnel used during joint assembly if any. Customary units. Most of the compression occurs in the gas- ket, but additional compression also occurs in the flange. Local flange distortion under the bolt als is important Subsequent tightening of individual bolts causes addi tional gasket compression and reduces the preload of previously tightened bolts. The difficulty is notin the formulas themselves but in accurately pre- dicting the all-important friction coefficients upon which the calculations depend.

Surface friction conditions can vary widely due to factors such as relatively loose man facturing tolerances for standard threads, thread condi- tion issues, new versus reused bolts and nuts, the presence of hardened washers versus turning on the flange face, variations in nut dimensions, and the pres- tence of coatings and lubricants.

Additional information on torque formulas and the effect of friction factors may be found in the Handbook of Bolts and Bolted Joints. This formula applies to standard deg. While the nut factor method does not address all of the variables that can affect the torque-preload relationship, it produces similar and fully acceptable values forthe assembly of flanges under this Guideline.

The value of K in most applications at ambient temperate is generally considered to be approximately equal to the Coefficient of friction plus 0. Based on the above, friction coefficients of 0.

Itis worthwhile to note the sensi- tivity of obtained load to an applied torque from rela- tively small changes in nut factor For example, a change from 0.

Insufficient application of lubricant to the working surfaces will have the effect of adding: significant variability to the obtained bol load. In addition, the maximum temperature listed by the manufacturer for a given antiseize product has not been found to be a reliable indicator that the product will improve disassembly of the joint after operation at elevated temperature.

Once again, itis recommended that test results on similar materials andl operating com- ditions be sought to guide the user on the appropriate product to be employed in a given service. Use of these washers under the head of a bolt may lead to interference with the bolt shank or underhead file. Also, ASTM F does not provide dimensions for certain nominal sizes needed for pipe or vessel flanges.

This Appendix does not con- tinue the use of this material due to material cost and manufacturing concems. Discontinuation of the use of SA material does not imply that this material is technically deficient M The Type 6 washer material isa precipita- tion hardening stainless steel that has increased corro- sion resistance as compared to Type 5 washer material.

M24 Scope M Arc and gas cut washers shall be free of metal spatter, M Critical issues increase with the criticality of the joint and therefore the fastener cost factor usually remains. This does not include tightening the fastener again as, in to tum the nut to a tighter position from a static position, reuse: to use more than once, tighten: apply load to the threaded fastener system, through some means of turning of the nut or direct tension.

The fastener system materials, quality, and condition have a large influence over the total outcome. This is why torque is successful for many applications. The surfaces and friction change and therefore their performance is forever changed. Each subsequent engagement of the same threads will pro- luce similar results until an optimum or dition occurs. Since the flange determines the grip length effective stretching length , the same threads are always being worked, 2 In the case of bolts without integral head, itis virtually impossible to work and rework the same threads given the current workforce practices.

When it becomes necessary to reuse bolts without integral heads, strict control is advised to ensure that the threaded fas- teners are correctly installed with some means of determining that you are working the same threads. However, crating, similar and fairly predictable conditions on a group of fasteners is more practical.

Starting with new threaded. For larger diameters, it is recommenced that the cost of cleaning, deburring, and reconditioning be compared t0 the replacement cost and considered in the assessment of critical issues of the assembly. Strong consideration should be given to replacing bolts of any size should it be found that they have been. The detailed procedures provided in this Appendix are intended for flange joints for which controlled assembly :methods are to be used.

Provisions are made for both a simple approach and for a joint component approach, In some rare cases, this may not be the case, and the limits should then also be checked at both the ambient and operating. For most standard applica tions, this will not be necessary.

These additional modes of faihure may. The assembly bolt stress should not be high enough to cause over. The specified bolt stress should be below the bolt yield point, such that bolt failure does not occur: In addition, the life of the bolt can be extended by specifying an even lower load.

The assembly bolt stress should be selected such that permanent deformation of the flange does not occur. Leakage due to flange rotation may be due to concentration of the gasket stress on the gasket outer diameter causing damage or additional relaxation.

Further integrity issues, as outlined in the following section on the joint component approach, may also be considered, as deemed necessaty. This value is intended to elimi nate damage to the bolt or assembly equipment during assembly and may vary from sit to sit.

This values intended to provide a lower limit such that bolting inaccuracies do not become a significant portion of the specified assembly bolt stress, Shs. The maximum permissible bol stress for the Mange Sfau must be determined, based on the particu: lar flange configuration. This may be found using either elastic closed-form solutions or elastic-plastic iit ee- ment analysis, as outlined in section O Any value provided should inchide consideration of the effects of flange rotation for the type of flange being considered in increasing the gasket stress locally on the outer diameter.

This value isthe minimum recommended. The value is the stress that the gasket should be assembled to in order to obtain, adequate redistribution of any filler materials and, ensure an initial seal between the gasket and the flange faces, i The minimum gasket operating stress Sgmino must be obtained from industry test data or from the gasket manufacturer. This is the gasket stress that should be maintained on the gasket during operation in order to ensure the leakage does not occur.

A default value of 07 may be used if data are not available, Step 1: Determine the target bot stress in accordance with eg. Shas S Sf ae! A table of assembly bolt torque values can then be caleu- lated using eq. O-2M or An example table of assembly bolt stresses and torque values using this approach is outlined in Tables O-8 and O-9, respectively.

A mote complex restonship forthe operational gasket stress may be used in ew of this equation that incudes te Sects of elastic interaction in changing the bolt ses. Since this bolt stress is approximate, and the flange material yield tends to be lower bound, itis considered appropriate to use these limits without modification or additional safety factor. Anexplanation ofthe limits and equations used to deter.

Su TH 0. Consider eiferent bot or nut materia eg, avid stainless nus on stainless bls or increase hard ness eference between them Io exceed 50 HEW 2 Consider through-tardened washers. Se Append M. See section 6 Use improve assembly procedure and qualified assembles See section 11 and Append A. See Appends 2 of Section il, Dhsion 1 2 consider ot torque ste dung warmup.

Simply mal, phone, fax or Email ws and a Customer Care representa wl anal your request. You might also like Atlas Engineering Metals Handbook. Bolt Torque Calculation for Flange. Ansi Valve Leakage Standards. Bolt-tightening Handbook. Flange Management Procedure Fix – Copy. Fracture in Brittle and Ductile Materials. Torque Values. Bolt Tightening Torque. API 5th vs 6th Final. API calculation. ISO

 

Asme Pcc-1 Bolted Flange Joint Assembly [3noeo0yld]

 

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Download Free PDF. Salvador Mendoza. Related Papers. Nsen V Piping Handbook 7th Edition. Process piping guide R2. There will be no addenda issued to this edition. ASME issues written replies to inquiries concerning interpretations of technical aspects of this document. This code or standard was developed under procedures accredited as meeting the criteria for American National Standards.

The Standards Committee that approved the code or standard was balanced to assure that individuals from competent and concerned interests have had an opportunity to participate. The proposed code or standard was made available for public review and comment that provides an opportunity for additional public input from industry, academia, regulatory agencies, downloac the public-at-large. ASME does not take any position with respect to the validity of any patent asm asserted in connection with any items mentioned in this document, and does приведу ссылку undertake to insure anyone utilizing doownload standard against liability for infringement of any applicable letters patent, nor assumes any such liability.

Users of a code or standard are expressly advised that determination of the validity of any such patent rights, and the risk of infringement of such rights, is entirely their own responsibility. Participation by federal agency representative rownload or person s affiliated with industry is not to be interpreted as government or industry endorsement of this code or standard. ASME accepts responsibility for only those interpretations of asme pcc-1 free download document issued нить download dino crisis 2 for pc free full version про accordance with the established ASME procedures and policies, which precludes the issuance of interpretations by individuals.

No part of asme pcc-1 free download document may be reproduced in any form, in an нажмите сюда retrieval system downloas otherwise, without the prior written permission http://replace.me/17533.txt the publisher. The scope of this committee was to develop and maintain standards addressing common issues and asme pcc-1 free download related to post-construction activities and to work with other consensus committees in the development of separate, product-specific codes and standards addressing issues encountered after initial construction for equipment and piping covered by Pressure Technology Codes and Standards.

The BPTCS covers non-nuclear boilers, pressure vessels asme pcc-1 free download heat exchangerspiping and piping components, pipelines, and downpoad tanks.

The PCC selects standards to be developed based on frew needs and the availability of volunteers. Other topics are under consideration and may possibly be asje into future guideline documents. The subcommittees were charged with preparing standards dealing with several aspects of воскресення winnie mashaba videos download таким in-service inspection xownload maintenance of pressure equipment and piping.

If it is determined that repairs are fdee, guidance on repair proce- dures is provided in the appropriate portion of the Repair asme pcc-1 free download Pressure Equipment and Piping Standard PCC To provide all stakeholders involved in pressure equipment with a asme pcc-1 free download to identify publications related to pressure equipment integrity, a Guide to Life Downlaod Management of Pressure Equipment Integrity has been prepared PTB None of these documents are Codes.

Lang, Asme pcc-1 free download. Sims, Jr. Antaki, Becht Engineering Co. Batey, The Dow Chemical Co. Inspectors C. Reynolds, Pro-Inspect, Inc. Chaku, Lummus Technology, Inc. Hayman, Consultant S. Koves, Retired C. Rowley, The Wesley Corp. Lang, FM Global J. Lay, Hytorc K. Oyamada, Delegate C. Leonard, Life Cycle Engineering T. Tahara, Delegate K. Mokhtarian, Consultant C. Neely, Becht Engineering Co. Neely, Chair, Becht Engineering Co.

Milne, Hydratight B. Hayman, Consultant J. Waterland, Virginia Sealing Products, Inc. The bolted flange joint assembly BFJA guidelines See section F-2 of Appendix F for pccc-1 asme pcc-1 free download described in this document apply to pressure-boundary downnload flange joint assembly procedures not currently flanged joints with ring-type gaskets that are entirely listed in these guidelines.

Before assembly is started, downlpad and examine flange Guidance on здесь BFJAs not providing and fastener contact surfaces as asme pcc-1 free download здесь this section.

Avoid using A BFJA is a complex mechanical device; therefore, carbon steel brushes on stainless steel flanges. One of the activities essential to leak-free per- with flexible graphite filler is to be used as the replace- formance is the joint assembly process. The guidelines ment gasket. It is face finish see Appendix C and for damage tree surface recommended that written procedures, incorporating finish such as scratches, nicks, gouges, downlooad burrs.

Asme pcc-1 free download the features of these guidelines that are deemed suitable tions running radially across the facing are of particular to the specific application under consideration, be devel- concern. Refer to Appendix D for guidelines covering oped for use asme pcc-1 free download the joint assemblers. Alternative features recommended limits on gasket contact surface imperfec- and methods for specific applications may be used sub- tions and their locations.

Appendix Asme pcc-1 free download provides recom- agent provide, or arrange to have provided, as appro- mended final surface finishes.

Notes leak histories or suspect fabrication, it is recommended to check gasket contact surfaces of both joint flanges for 1 Rules for design of bolted flanges with ring-type gaskets are flatness, both radially and circumferentially. Any fastener with asme pcc-1 free download dimensions essary when tolerances need to be tight. Appendix D less than the minimum major diameter or the minimum provides flatness tolerance recommendations.

Appendix C provides recommended Appendix N provides supplementary fres on final surface finishes. Likewise indicated by uneven wear asme pcc-1 free download, etc. Roughness, asme pcc-1 free download, and protrusions tapped asme pcc-1 free download threads. On severely covers repair of damaged tapped hole threads.

If sepa- damaged flanges, machining this area may be required, rate washers are scored or cupped from previous use, in which case the minimum acceptable residual flange replace with new through-hardened washers 3 thickness must be considered.

The use of through-hard- surface-hardened washers are not suitable. Downloda results in maximum diameter asme pcc-1 free download ame when bolt load-control meth- sealing surface contact, maximum opportunity for uni- ods asme pcc-1 free download as torque or tension are deemed necessary see form and design-level gasket loading, and reduced fric- Appendix N.

For larger bolt diameters, it is recom- tion between the nut and the flange. Guidelines for mended that the cost of cleaning, deburring, and recon- aligning flanged joints are provided in Appendix E. When absence of or having made correction for unacceptable diwnload bolts are used, the remaining corrosion protection gasket sealing surface imperfections and flatness toler- and self-lubricating aske are additional considera- ance deviations, as well as joint alignment considera- tions with respect to continued use or downloaf.

See tions see Appendices D and E. One and 7 f. Use of gaskets so refurbished is not considered 3 Thread dies generally do not result in a smooth, as gasket reuse in the context of the first sentence.

For reconditioned surface; therefore, turning bolt threads in other gasket types, experience has clearly shown that a lathe is the preferred method to recondition costly only a new gasket will reliably provide the necessary fasteners. The process взято отсюда remove thread material; plastic deformation downlpad elastic recovery characteristics therefore, the user is cautioned to ensure the tolerance essential to achieve an effective seal.

However, it is generally recognized for the nuts. These are important considerations when torquing that the use of through-hardened steel washers will improve the methods either manual or hydraulic are used for bolt tightening. See Appen- Flat washers also promote improved load distribution.