PCC-1-2013

Prévia do material em texto

Guidelines for
Pressure Boundary
Bolted Flange Joint
Assembly
AN AMERICAN NATIONAL STANDARD
~ The American Society of
~ Mechanical Engineers Two Park Avenue • New York. NY • 10016 USA
Date of Issuance: November 12, 2013
This Standard will be revised when the Society approves the issuance of a new edition.
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document. Interpretations are published on the ASME Web site under the Committee Pages at
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without the prior written permission of the publisher.
The American SOcietyof Mechanical Engineers
Two Park Avenue, New York, NY 10016,5990
Copyright Cuidnnce on Troubleshooting Flanged Joint Ll'to ~--:--------
(Name)
Il)
I II
ASME PCC-1-2013
again, and Lay)
ASME PCC-2-2011, Repair of Pressure Equipment and
Piping
Publisher: The American Society of Mechanical
Engineers (ASM E), Two Park Avenue, New York,
NY lOO'J6-5990; Order Department: 22 Law Drive,
P.O, Box 2900, Fairfield, NJ 07007-2900
(www.asme.org)
16.4 ASME Boiler and Pressure Vessel Code, 2013
Edition
Section II, Pari' A - Ferl'OUS Melteria I Speci fications:
SA-I05/SA-I05M, Specification For Carbon Steel
Forgings for Piping Applications
SA-182/SA-182M, Specification for Forged or Rolled
Alloy and Stainless Steel Pipe Flanges, Forged
Flanges, and Valves and Parts for High-Temperature
Service
SA-'193/SA-193M, Specification for Alloy-Steel and
Stai nless Steel 801 ti ng Ma ter ials for High-
Temperature or High Pressure Service and Other
Special Purpose Applications
SA-194/SA-194M, Specification for Carbon and Alloy
Steel Nut!> for Bolts for High-Pressure or
High-Temperature Service, or Both
SA-240/SA-240M, Specification for Chromium and
Chromium-Nickel Stainless Steel Plate, Sheet, and
Strip for Pres ure Vessels and for General Appl ications
SA-453/Sf\-·153M, Specification for High-Temperature
Bolting Materials With Expansion Coefficients
Comparable to Austenitic: Steels
SA-540/SA-540M, Specification for Alloy-Steel Bolting
Materials ror Special Applications
20
ASME PCC·t-20B
SA-693, Specification for rr~cipitation-HMJening
Stainless .md Heat-Resisting Steel Plate, Sheet, and
Strip
Section II, Part B - Nonferrous Material Specifications:
S8-637, Specification for Precipitation-Hardening
Nickel Alloy Bars, Forbings, and Forging Stock for
High-Temperature Service
NOTE: ASM£ C;i\ and 56 m.HNi.ll specification- are used in
i\"ME pec·t A..,lf-I matenal -pt:Uh(.lllons ma) .11-;0be u-cd or
l.ll-..,nto apply, .1' allowed by the JPplicable cod", 01 construction,
Inr [he joint b~in!; considered.
Section VIII, Division I - Rules for Construction of
Power Boilers
Publi her: The American Society of Mechan ica l
Engineers (ASME), Two Park Avenue, New York,
NY 10016-5990; Order Department: 22 Law Drive,
P,O, Bux 2900, Pairfield, NJ 07007-2900
(www.asrne.org)
16.5 ASTM Publications
ASTJ\I A829/ A829M-06, Standard Specification for
Alloy Structural Steel Plate!'>
ASTM F436-'II, Standard Specification for Hardened
Steel Washers
ASTrvl F606-11 a, Standa I'd Test Methods for
Determining the Mechanical Properties of Externally
and Internally Threaded Fasteners, Washt!rs, Direct
Tension indicators, and Rivets
ASTM F606M-'13, Standard Test Methods for
Determining the Mechanical Properties of Externally
and Internally Threaded Fasteners, Wa~hers, and
Rivets (Metric)
Publisher: American Society for Testing and Materials
(ASTM International). 1(l0 Barr Harbor Drive,
P.O. Box C700, West Conshohocken, PA 19.+28-2959
(\\ ww.astm.org)
16.6 AWS Publication
AWS A5.1.f/A'U-!M:2011, Specification for Nickel and
Nickel-AII(IY 13for
Vessels ASME Code Section VIII, Divisions 1assemblers
in accordance with the recommendations contained in
ASME PCC-l but has 110tyet received training and quali-
fication from a Qualifying Organization.
/It)lling trainee: a person undergoing training to become
a Qualified Bolting Specialist.
current edition: the edition of the referenced code or tan-
dard that is specifically cited in ASME peC-l or was
in effect at the time of publication of this version of
ASME PCe-1.
111'11/ exc!wlIgcr/tll/'I'.,ilt"1'1 ioiuts: gasketed bolted joints that
comprise the pressure-boundary closure between the
tubesheet and the mating shell and tubeside girth
flanges and that require special assembly considerations
(see para. A-2.3.3). The gaskets for these joints axe gener-
ally located entirely within the circle enclosed by the
bolt holes, with 110contact outside this circle; however,
this is not intended to evclude other configurations, such
as flat-faced flanges, fmlll this Appendix.
Inelllsiry Orsnlli:;a/ioll: :111 organization that represents
the interests of users of bolted joint assemblers.
lotos! cdiilon: the latest edition in effect at the time of
reference.
Mntl'rinl SI~fCly Oil/II SIIt't'1 (MSDS): a data sheet for chemi-
cals that define ...important information such as the levels
of toxicity, flammability, and first-aid actions required
personal protcctit»: t'I/lIilllllt'1I1 (prE): the safety equipment
(safety glasses, safety boots, earplugs. etc.) required to
perform the assembly task,
pipillg jt1ill/S: similar 10 pressure vessel joints; however,
considerations relating to alignment and external load-
ings on the joints con govern design and assembly
I 11
requirements. The gclskdthan half of the aspects
covered in the training outlined in para. A-2.3. The expe-
rience should be documented by references from Senior
Bolting Assemblers, Qual; tied Senior Bolting Specialists,
or Qualified Bolting Specialist Instructors indicating that
the field experience obtained meets the requirements of
thts Appendix. An example reference sheet is supplied
in Form A-1. At least om' reference should be from"
supervisor at the individual's current or previous place
of work. An individual mily obtain "he field experience
2(,
11 , .
ASME PCC'1-2013
Form A-1 Example Reference Sheet
ASME PCC-1 Appendix A Qualification: Confirmation of Work-Site Experience
Please type or print legibly and return to the applicant
INSTRUCTIONS
APPLICANT: Complete items 1 and 2, then forward this form to the individual serving as your work-experience reference.
All work-experience references must have worked with you at least during the time period being validated.
REFERENCE: The following Individual is applying to receive qualification as a Bolting Specialist per the quatilications and
requirements outlined in Appendix A of ASME PCC-1. Your name has been given as a reference to verify the required
Minimum Work Site Experience. The ASME PCC-1 Appendix A Qualifying Organization is charged with the responsibility of
qualifying only those individuals who have demonstrated a proficiency in the assembly, operation, and quality assurance of
bolted joints. Your assistance in helping make that determination is appreciated.
Applicant Information
1. Applicant's name:
(First) (Middle) (last) rs., Jr., III)
2. Mailing address: _
(Street address)
(City) (State) (Country) (Postal code)
Reference Information
3. Reference's name:
(First) (Middle) (Last) (Sr., Jr., III)
4. Mailing address: _
(Street address)
(City) (State) (Country) (Postal code)
5. Work phone: Home phone: Email: _
6. Are you a (select one)
__ Senior Bolting Assembler? I I No J Yes
If yes, state experience: _
__ Qualified Senior Bolting Specialist? _ No Yes
If yes, Qualifying Organization and number: Expiration date: _
__ Qualified Senior Bolting Specialist Instructor? _ No _ Yes
If yes, Qualifying Organization and number: Expiration date: _
27
F 1. 11
ASME PCC-1-20l3
Form A-1 (Back)
7_What is your business relationship to the applicant? _
8. How many years have you known the applicant? _
9. Keeping in mind the Intent to ensure that applicants for Bolting Speciallst qualification have broad, prio: Walk-site
axoertence in bolted jolm assemblv that meets the intent of ASME PCC-1 Appendix A, para. A-2.2:
(a) Do you centum that lhe I.lpplicant has worked In the field with the assembly of bolted [olrus rOI (pIIH1SB check one)
at least 6 months full-lime, with frequent joint assembly on a daily basis?
No Yes
at least 1 year with infrequent joint assembly, with intense periods occurring at least t week per month and
at least a total of one-third 01 the time worked In thaI year?
No Yes
at least 2 years with multiple, sporadic periods of joint assembly?
= No _ Yes
(b) In vcur estimation, has the applicant's bolted joint assembly work experience been sufficiently broad for him/her
to develop a wide range of skills and knowledge necessary to form the foundation for further training and ultimate
qualification as a Qualified Bolting Specialist?
No Yes
10. Do you recommend the applicant for qualification as a Qualified Bolting Specialist? - No IYes
11. Signature of reference: _ Date: _
28
F • I [..
ASME PCC-1-2013
subsequent to completion of the training, in which cave
they are not considered qualified until such time ,,::.they
have sufficient experience to obtain their qualification.
In the case of an individunl with either powered equip-
1111'1 It, heat exchanger, or special joint supplemental qual-
ifications, the experience shal! include o1t leosr one-
quarter of the time spent "(Irking on those item ... of
equipment. Where the [requency of working on such
equipment i" less than thb, the time period prior to
achir-v ing the supplcrnentul qualification :-11.111be
t').tcntil'd until an equivalent period has passed.
A·2.3 Training of Fundamentals
rlw Qualified Bolting Speciallst shall h.:l\ e "dl!llllatc
tr.,ining (In the fundamental-, of the as ernblyoperation,
and quality assurance (If bolted joints. Pr.ictical and the-
oretlcal 1')\,ll1lin(ltions shall be p;iven at the end IIf "ul'h
tr.linillg tll ensure, to till;' sntio.,lnction of a Qualified
Bollillj..; SI'L'Litilist lnstrurtur, II,ot the C,lndidntL' hurIJct's, and job saft!ty analysis,
including
(I) c('mmon pl'llCCdurl's for ,,"ork permit:. Jnd
ensuring system isoliltion
(21 finger pinch point-. with assembly am.I t'L' section 6, subpara. (c)
(6) ba ...i joint alignment equipment (pry-bar, drift
pins; see Appendix E)
(7) bitl' or corporate guulelines
(c) tilt' principles of bolt dl1ngation, bolt load, .1I1d
gasket stress
( I) 1,·I.ltion"hip bet ween bolt .,tr6 (neep/rela""tion and
operatlng conditions) on joint leakage and overall loint
rei iabi IitY
(c) gasket types and therr limitations
(I) summary of cnrn mnn g.1sket lYrl'S ,Ind
materials
(2) sensitivity of (iiffel'l'lIt g.\~kl'l·types to assembly
procedures
(3) maximum allowable ~asket stress
(4) minimum requirt'd g,)'.;kel stress
(5) a\\ areness of tlw need fClr ci)l.'IIli.:.11
comp.ltibil iIY
(6) awnnml:'SS of templ·r.llurl! limits
(j) bolt types and their IimitilLil1ns
(I) brief detail of common bolting specifictltillns,
includingyield strength
(2) nut-bolt combinations, nut strength \ ersus bolt
strength
(3) generic material temperature limils
(4) materials for stress-corrosion-cracking
environments
(5) corrosion resistance
(6) coi~tthe ,)',:'1.'111-
bly process and ma) have the capability to improv e bolt-
load ,lCLl1r..p,1I1...ion joints
(c) tightening piping joint" on pres...ure rt:'lil'f dt'\ 'l'I'~
(I) potential for inspection work-hold poi nt 111
enl>LI1'Ctl hIt Ihere is no hlockilgc in lilt' I'd ief path
(2) correct installation. g,hkl.'h, handling. .ind ol'i-
entation of rupture discs and dl~chMge lines
(3) confirmation of piping status by curt if icclinspector (if required)
(d) tightening piping joints on and around piping
expansion joints and spring hangers with cold-set
(1) methods of safely restr"lining bellows and cold-
set spring hangers
(21 ensuring restraints are removed prior to
operation
(3) how ttl recognize ant] report if too much force
is required to bring the flanges together (seeAppendix E)
(c) importance of alignment and gnp uniformity
(1) Appendix E flange alignment tolerances
(2) tighter limits required for shorter or stiff spans
(3) importance of the bolt-, passing freely through
the bol t holes so that the nuts rest parallel to the Hange
if) selecting the target bolt-assembly load
(1) parameters that determine appropriate bolt
load (flange size, gasket type, nange class, flange type,
flange material, bolt material, piping service)
(2) deterrnina tion of correct load from gasket speci-
fications hand torque
wrenches, torque multipliers, and impact wrenches
n) where to look for guidance (user spccification-.
comp.lIl), guidelines, tool manufacturer Web sues)
A-2,3.2 Additional Training Required to Obtain a
Powered Equipment Supplemental Qualification. 'l lu-
curriculum sl':111ensure candidates have a thorough
undcl':.talllling of the fOllowing :1spectly, .I~st'mbl)', and tiglrtl'l1ing used:
(II) genl'ral he.llth and !>afety prl'l.i1utions
(7) .,,)(ety Clnd securing (It high-pressure fluid", fi 1-
ting~, llllli hoscl> during ()pl'r,ltiull
31
ASME PCC·1-2013
(2) placement a nd removal of backup wrench under
high loads
(.3) pincb points relative to hydraulic or pneumatic
torque equipment and backup wrenches
(4) dangers associated with socket failure under
load from using the incorrect or a low-quality socket
([I) hydraulic and pneumatic torque joint tightening
0) working parts of hydraulic and pneumatic
torque equipment
(2) working parts of a hydraulic pump and
hydraulic/pneumatic regulator
(3) troubleshooting hydraulic wrench, hose, hose
connections, and pump failures
(4) method of setting target torque
(5) method of using a hydraulic torque wrench
(6) single-point tightening versus simultaneous
multiple-point tightening, and influence on the assem-
bly procedure
(c) joint tightening using tensioning equipment
0) working parts of a hydraulic bolt tensioner
(2) working parts of a hydraulic pump and hydrau-
lic regulator
(3) method of setting correct bolt load (formulas
for calculating the target bolt load) for the number of
tools in relation to the number of bolts in the joint
(4) method of using a hydraulic bolt tensioner
(5) troubleshooting of rensioner, hose, hose connec-
tions, and pump failures
(6) use of a single tensioner versus simultaneous
use of multiple tensioners and the influence of each on
the assembly procedure (see Appendix L)
(7) effect of elastic recovery (indicated tensioner
load in relation to final bolt load, need for overtension.
and the effect of bolt grip-length to bolt-diameter ratio:
see para. 8.2.2)
(d) calibration and maintenance of hydraulic bolt-
tightening equipment
(1) requirements for maintenance of common
hydraulic field equipment
(2) inspection of hydraulic hoses and cylinders
(3) familiarization with methods for calibrating
common hydraulic field equipment
(4) importance and frequency of calibration
(e) selecting appropriate bolt-tightening tooling
(1) acceptable methods in relation to bolt size
(2) naturally occurring clearance problems related
to general styles of tooling such as hydraulic in line ratch-
ets, hydraulic square-drive ratchets, fixed-size tension-
e rs, variable-size tens io ners. hydraulic nuts, and
mechanical jack nuts
(3) bolt-load limitation of hydraulic tensioners as
related to pressure, ram size, bolt size, and bolt length
(4) use of comparative angle of nut rotation method
when standard hydraulic tooling will not work (insuffi-
cient space for hydraulic equipment for one or two bolts)
A·2.3.3 Additional Training Required to Obtain a Heat
Exchanger Supplemental Qualification. The curriculum
shall ensure candidates have a thorough understanding
of the following aspects of joint disassembly, assembly,
and tightening for exchanger joints, As a minimum, the
following shall be addressed:
(aJ types of exchangers [Tubular Exchanger
Manufacturers Association (TEMA) designations] and
their joints
(1) joint configurations, terminology, and locations
(2) gasket configurations for the different types
of joints
(3) confined gaskets versus unconfined gaskets
(4) measurement of final joint gaps as a measure
of success
([/) bundle pushing and considerations for assembly
(1) bundle and channel orientation to align piping
and pass-partition groove(s)
(2) risks during pushing (damage to the flange-face
or shell gasket)
(c) tubesheet joint considerations, shellside gasket
damage, and recompression of shellside gaskets on tube-
sheet joi.nts
(1) second gasket compression (more assembly pas-
ses may be required)
(2) risks if the shells ide gasket seal is broken when
the channel is removed (if bundle is not bei.ng pulled)
(3) inspection of pass-partition surfaces (pass-
partition flush with flange facing)
(4) consideration of tightening shoulder-type bolts
from both sides
(5) gasket pass-partition alignment
(d) Breechlock exchangers (optional)
(1) general sealing configuration of Breechlock
exchangers
(2) special procedures for assembly of Breechlock
(manufacturer's instructions)
A-2.3.4 Additional Training Required to Obtain a
Special Joint Supplemental Qualification. The curricu-
ILLOl shall ensure candidates have (I thorough under-
standing of all significant aspects of joint disassembly,
assembly, and tightening for special joints. A compre-
hensive listing of the requirements is outside of the scope
of these guidelines. However, the general approach used
in the previous sections for piping and exchangers
should be followed in formulating a training curriculum
for specie I joints. The following general sections shou ld,
as a minimum, be covered:
(a) seal surface preparation
(b) the importance of alignment and gap uniformity
(c) gasket handling, preparation, and installation
(d) specific assembly steps, tooling, or procedures
pertinent to the joint in consideration
(11) safety considerations, induding lockout, depres-
surization, electrical isolation, and special work permits
32
ASME PCC-1-20l3
A-2.4 Practical Examination
The Qualified Bolting Specialist shall demonstrate his
or her understanding in the assembly of bolted joints
by taking part in at least one of the following range of
bolted joint practical demonstrations and witnessing the
other demonstrations. The demonstrations are designed
to highlighl significant aspects of the training curricu-
lum and art' to be perfo: med i_11 the presence, and to the
is to be assembled uslng both hydraulic tensioning and
hydraulic torque equipment.
The following demonstration- are suggested to high-
light several critical points of joint assembly. Alternative
demonstrations or modifications to the outlined details
may be substituted for any of the demonstrations, pro-
vided the desired learning points are still achieved, as
judged by the Qualified Bolting Specialist Instructor.
A-2Al Importance of Gasket Placement
(a) Perform the following on a flange test rig having
[ou r or more bol ts:
(1) Assemble a four-bolt, small-diameter flange
with a spiral-wound gasket without inner and outer
rings, using a tightening pattern, and ensure that about
half of the gasket width is not on the raised-face portion
on one side.
(1) Assemble a class 300, four-bolt, small-diameter
flange with ,1 class 150 spiral-wound gasket with outer
rings, with the gasket in a vertical position, using a
tightenli1);; pattern, and en ure that the outer ring of the
(;asket is located against the bolts.
(3) Assemble a four-bolt, small-diameter flange
with a spir.rl-wound gclsket without inner and outer
ring", using a tightening pattern, and ensure the gcskct
i., centrally located on the raised face.
(b) Inspect each gasket after disassembly to demon-
strate uneven compression when not properly located.
A-2.4.2 Importance of Joint Alignment Prior to
Assembly
(n) Perform the following on a flange test rig having
fllur or more bolts and equipped with a spring system
that requires approximately 50':-;, l)f the assembly bolt
load on the t\\ o upper bolts to bring the tlanges into
prQper alignment:
(1) Assemble a joint with an expanded PTFE gasket,
without aligning the flanges first (use flange bolts to
align the joint),
(2) A semble a joint with an expanded PTFE ~askt't,
ali):,'11ing the Hanges using external means (e.g.. come-
along, chain-block),
(/I) After each assembly, observe the gasket compres-
sion and measure the final thickness of the gJ.;ket after
disassembly to demonstrule uneven loading when initial
a lignrnent of the flanges i...110t performed.
A-2.4.3 Importance of Bolt Assembly Pattern
(II) Perform the following on a Flange test rig having
four or more bolts:
(7) Assemble a four-bolt, small-diameter flange
with ,111 expanded PTFE ~asket without using .1 tight-
ening pattern (i.e., using circular posses only).
(2) Assemble a four-bolt, small-diameter flange
with an expanded PTFE go1~ket using a tightening pat-
tern per ASME PCC-I.
(b) Observe gasket appearance, and measure the final
thickness of the gasket after disassembly to demonstrate
uneven loading when cro s-pattern tightening is not
used.
A-2_4.4 Importance of Bolt Assembly Pattern and
Correct Gasket Selection. Perform the following test on
a flange test rig having eight or more bolts C~NPS 6):
(0) Assemble a joint with a spiral-wound gdsket with-
out inner and outer rings, without using a tightening
pattern (i.e., u'iing circular passes only).
(b) Assemble a joint with a spiral-wound gasket with
inner and outer rings, without using i1 tightening pattern
(i.e., using circular pa5~es only).
(c) Assemble d joint with a spiral-wound gasket with-
out inner and outer rings, usingrequirement of this Appendix. An example
reference sheet is supplied in Form A-l.
(C') have ready access to the lnrest edition of
ASME PCe-l, as well as workplace access to the current
editions of the documents referenced in para. A-1.3.
if) take an active role in bolted-joint failure analysis
arid identification and implementation of correct ive
action at the company or P"1I1t sites where he or she is
employed.
A-3.2 Duties
The duties of a Qualified Senior Bolting Speciillist
are identical to those of the Qualified Bolting Specialist
(para. A-2.5) with the addition of those described in
paras. A-3.2.1 and A-:U.2.
A-3.2.1 Administrative, The administrative duties
of ,1 Qualified Senior Bolting Specialist, include, but Me
not limited to, the following:
(II) providing on-the-job training to bolting asscru-
biers and bolting trainee"
3-1
ASME PCC'1-2013
(/I) m.untaining and ,'nal) 7ing records, including
those f,'r joint assembly procedures, inspections, and
Qualified llolting Specinlist performance. including
ml'dinl-> till' requirements of section A-2
(t') t"l~uring that Qualified St,lting Speddli~t." bolting
assemblers, and other personnel under hi., or her super-
vision pertorm their duties in accordance with the guide-
line-, of I\~ME PCC-I and "II applicable ~itc standards
and requirvments
(el) I'rl'parrng joint assembly procedures in accor-
dan«- with ASME I'CC-I
(e) I1hlintnining a workplace copy of the latest l'LJitioll
I)f J\SMF PCC-I, n... well ,I" the current edition of the
documents referenced in para. A·1.3
A-3.2.2 Technical. fill' technical duties of if
QlI"liflt'd Senior Bolti11!iSrp"ii1lbt include, but nrc not
limited to, the follO\\ in~:
(II) reviewing assembly procedures and inspection
repoi h, and ensuring l·n(()l'n·I111.'ntof legally adopted
rt'q u i remen I'!
(/I) reviewing applicntlon ...fl)l' waivers and variances,
and n1.1l...ingrecommendatrons, as required, 10 pmper
authorities
(c) en ..uri"g client review of joint assembly proce-
durcs and receipt (,f appropriate joint assembly
documentation
(d) investigating complaint ...and accidents
(c) helping to develop company policies and
procedures
(0 presenting on-site orientation courses tor both
Qualified Bolting Specialists and bolting assemblers
A- 3.3 Maintenance of Qualifications
A-3.3.1 To maintain the qualifications, o Qualified
Senior l30lting Specialist 'hall
(II) conform to the requirements of para. A-2.6.
(II) spend a minimum of 20').. of time working in the
field with Qualified Bolting Specialists, Qualified Senior
Bolting Specialists, trained bolting assemblers, trained
senior bolting assemblers bolting assemblers, or senior
bolting assemblers.
(c) fl":-.istwith the amendment of existing work-site
a ~l'l1lbly procedures deemed inadequate or unsafe, or
the dev elopment of revised \\ ork-site assembly proce-
durcs Ior unusual conditions or equipment.
(d) attest to his or her compliance with (a) through
(c) ,lilt! provide at least two references from co-workers
til' his or her employer LIP"" qualification and triennial
renewal of '(ut
,lnct' c\er)':l yr. TIlt' qUiflifi',1tion rt"newal rrocc~s shall
inch ,J,'A-4.3.l Ttl maintain the qualifications, a Qualified
Bolting Specialist Instructor Sh,'ll
(n) conform to tht! rl'quirements (1f pMa. 1\-3.3. and
a ttend or condlll t at least one professional-level seminar
01' wnrh.!>hop per yeill' relaled to on\' or more of the
dutit.'s described in para. A-4.2.
(b) spend a minimum (1f 10"" of w0rk time in the field
with thl.' Qualified BCllting Specialisb, Qualifif:d Senior
Bolting Specidli'lts, bolting assemblers, or senior boltillg
assemblers.
(c) atlest to his or her compliance lVith (i'I) and (b)
,1Ild provide at least two references fwm co-workers or
his or her employer upon qualification and trieJU1inl
r., r
renewal of qualification. At least one reference is to be
from a supervisor at the individual's current or previous
place of work.
A-4.3.2 The Qualified Bolting Specialist Instructor
shall be required 10 renew their qualification at least
once every 3 yr. I'he qualification renewal proce ...shall
include a statement of compliance with the requirements
of pcll'a, A-4.3.1 and shall include a short lest or quiz
designed to highlight any updates that have occurred
in the preceding :'I yr to the Training or Fundnmcnta!s
portion (para. A-2,3) of (his Appendix. If no chilnges
to p.ua. 1\-2.3 have occurred, then that portion \If the
qualification renewal process may be 01111111'1..1, The quali-
fiml'ion renewal process test format, and test content
o:;h.ll1be outlined in the Qualification Manual.
A-4.3.3 The Qualifying Organization is responsible
fur determining that the intii\ idual candidate 1have obtained, at a minimum, the level of competency
as defined by the required tmining and experience out-
lined in this Appendix.
(d) It assists users in evaluating the quality and level
of experience of contract labor,
However, for those goal" to be achieved, it may l1l'
necessary for user ... to accept varied Qualification
Programs given by different Qllillifying Organizations,
To achieve that level 01 acceptance, it is recommended
that the users identify Review Organizations that main-
tain an acceptable level of SM E knowledge and review
ability to ensure that the requirements of para. A-5.:!.3
37
ASME PCC·1-2013
are met to a level satisfactory til the user. Delegating the
responsibility of quality review to independent Review
Organizations maxim iNS the likelihood of portability
being achieved: minimizes reliance on user resources;
and allows endorsement of program!:> at the corporate,
rather than site, level of the user organization.
Idea II)" users w ill collaborate wi thin interne tiona I,
national, regional, or industry groups to identify accept-
able Review Organizations. l'his facilitates portability of
qualification anl(Jng those organizations and minimizes
the likelihood thatQualifying Organizations will require
more than one Review Organization to meet the require-
ments of the applicable users.
When a new Qualifying Organization seeks to be
accepted b)' a user, it 15 recommended that the user
primarily review and endor-se the associated Review
Organization, rather than each individual Qualifying
Organization.
A-SA Definition of Terms
A-SAl Subject Matter Expert. The objective in
selecting the 5MEs is to howe a knowledge and experi-
ence base to provide ;1 comprehensive review of the
Qualification Manual.
(n) Selection of SMEs should be based on the follow-
ing cri teria:
(1) knowledge - possesses knowledge in the field
of bolted joint assembly
(1) experience - has worked in the field of bolted
joint assembly
(b) The following factors may be useful in selecting
the SMEs:
(1) training - has documentation proving their
successful completion of training programs til bolted
joint assembly
(2) credentia I~and certifications - possesses a ppli-
cable and appropriate credentials or certifications, or
both, expected of all evpert in bolted joint assembly
(3) experience - yeMs of practical experience
A-S.4.2 Balance of Knowledge. The composition of
the review team should include at least one of each of
the following 5MEs:
(n) an individual with sufficient experience ami
background to qualify as a Qualified Senior Bolting
Instructor
(ll) a mechanical or structural engineer with experi-
ence in the a sernblv, maintenance, and operation at
bolted joints
(t) a mechanical or structural engineer with expert-
once in the design and analysis of bolted [oints
A-5.S Program Effectiveness
To track the effectiveness of the Qualification Program
offered, the Qualifying Organization should collect dat,
from users, or their designees, I'(!gcm.iing the success of
the program.
For the purposes of thil, .1,1 "'int-li);hkning .lctl,·ilil.'s
,)lIt'e the "nil i~hilly 0pl·r.,1 iMIoII.
lto! lotuur: sec s/arl-IIII 1"'/0/'1/1/(',
lillt' figlt/l'IIillg: t'ighlcningand the Subcommittee
Oil PI11Iv I~V.lll1.,tion in IlJ95. In 1C)t)R,a Task Group under 11'1(-'pec began prq)iw1tion or Guidelines
for Pressure Boundary Bolted Flnngl' Joint Assembly and in 1999 the Subcommittee on Repair
and Testing W,1;, formed, Other topic') are under consideration and may possibly be developed
into future guideline documents.
TI1e subcommittee" w crc charged with preparing standards dealing with several aspects of the
in-service inspection and maintenance of pressure equipment and piping. GlliridiJlt's far Pressure
BOlIl/dary Bol/ed Flal/ge join! Assembly (PCC-I) provides guidance and is applicable to both new
and in-service bolted flange joint assemblies. The luspectiun (>Imlllillg U.,illg Risk-B(/st'd AldJ/()d$
Standard (rCC-3) provides guidance on the preparation of a risk-based in ...pection plan. Imperfec-
tions found at any stage of assembly, installation, inspection, operation, or maintenance are then
evaluated, when appropriate, using the procedures provided in the Fitncss-For-Seruice Standard
(API 579-1/ ASlV£E FFS-l). If it is determined that repairs are required, guidance on repair proce-
dures is prOI ided in the appropriate portion of the Repair of Prcs-ure Eouipntcn! and Pipill.'? Standard
(PCC-2). To provide all stakeholders involved in pressure equipment with a guide t(l identify
publications related to pressure equipment intt'grity, a Guide Iv L.ifl! Cye/I' MIl IIII,(:CIIII'II I' of Pressure
Euuiptueu! IlIlt-gl'ity has been prepared (PTB-2).
None of these documents are Codes. They provide recognized and generally accepted good
practices that may be used in conjunction with Post-Construction Codes, such o o.; API 510, API 57(1,
and NB-2..1, and with jurisdictional requirements,
The first eLii tion of ASM E PCC-I, Cllitlr!lillt.'S Ii". 1'1'4::55111'1'BrJllllt/nl'!J IJollet! FlllllSt' Joilt! IIS~l'lIIl1ll/,
w.....approved lor publication in 2000, The 2010 revlslon WsrtrilyhI' suitable for nil applications. l'rec:,\Utiontructed lJFJAs. It is
, Rules for dl'~igl1 of bolted flange!- with ring-type g~8keb are
,-,w..:wd in M,IIl;JHot bolting is also an option, but there is
a higher associated risk with that activ it) due to the
associated reduction in gasket stress if the tightenmg is
performed while the joint is pressurized. Live tightening
..hould not be considered the same as start-up retorque.
which is performed as part of the assembly operation;
live tightening is an operational activity that may be
performed on a periodic basis to recover relaxation (typi-
cally on high-temperature joints that have a history of
leakage) or as a reaction to ioint leakage. An engineering
and risk ana lysis l)f the Iive-tightening operation should
be carried out to establish that the operation can be
performed safely, Refer toASME PCC-2 for further infor-
mation on joi nt-tlghtening activities once the unit is FulIy
operationa I.
odd-bo/lillg: see hal] Im/t;'lg.
011/;'1(, ligith'lliIlX: st'e live Jigilll'lIillg.
start-tu) rctorquc: tightening l'rV1l:es)or 10 rest',' I 1.S mm (Y16 in.)
NOTE:
(1) Finishes listed are average surface roughness values and apply to either the serrated concentric or
serrated spiral finish on the gasket contact surface of the flange.
41
ASME PCC'1-20B
APPENDIX D
GUIDELINES FOR ALLOWABLE GASKET CONTACT SURFACE
FLATNESS AND DEFECT DEPTH
0-1 FLANGE FACE FLATNESS TOLERANCES
F'>dStil1g industry Ilnlness tolerance lirnits ' do not
include an .1%eS.,rnL'JlI(I( till' ability of the gasket II)
tolerate irnperfectruns. I he Illl~I','I1CeS in Table 0- J M 1
D-( are dependent on the t) pc (If g"s!..et employed and
oUe c.,legorizeJ based on the initial ax ial compression
of the gil"ket 10 the filial ,I~"elllbled load.
So(l gaskets (see Append», 13)Me more tolerant of
Ililn~..: flatness implc'rfl'( tion., hut are Iypic.llly more dllfi-
cull to assemble, Hard g.l,>k('[-; (:-t!e Appendix B) have
II'SS compression 111,111soft g'I'ikt!I'> and, while lhi~ can
help with improved assembly due to less bolt interaction
(cross-talk), it generally means that hard gaskets arc
111\11\' sensitive 10 J'lnll).;l} (1,1111"F',,,if,c.)hon Ior VI"'l'l, , il.lr Buill'r .1"" rl~,,~url' VI!"d {.Ildl·
5 31'1/4 Not allowed Not allowed
GENERAL NOTES:
(a) See Figs. D·3 and 0·4 for description of defect measurement
and for definition of w.
(b) Defect depth is measured from the peak of the surface finish
to the bottom of the defect.
--15
L. II .,'t, Ipl I. I J n v. ...1 1 J '.1.01111 At! ~'''II "
ASME PCC-1-2013
Table 0-2 Allowable Defect Depth vs.
Width Across Face (U.S. Customary)
Measurement Hard-FacedGaskets Soft-Faced Gaskets
fd )W/4 Not allowed Not allowed
GENERAL NOTES:
(a) See Figs. 0·3 and 0-1, for description of defect measurement
and for definition of IV.
(b) Defect depth is measured from the peak of the surface finish
to the bottom of the defect.
Fig. 0·3 Flange Surface Damage Assessment: Pits and Dents
Pits and dents
w
Do not locally polish, grind. or buff
seating surface (remove burrs only)
rd= projected radial distance across
seating surface
d= radial measurement between
defects
w = radial width of gasket seating
surface
Scattered; rs= the sum of rdi
46
ASME PCC-1-201)
Fig. 0-4 Flange Surface Damage Assessment: Scratches and Gouges
w
Do not locally polish, grind, or buff
seating surface (remove burrs only)
'd = projected radial distance across
sealing surface rd
Fig. 0-5 RTJ Gasket Seating Surface Assessment
t
d
_L
47
r
ASME peC-1-20l3
APPENDIX E
FLANGE JOINT ALIGNMENT GUIDELINES
e-i GENERAL
Proper alignment of all joint members is the essential
element of flange joint assembly. It results in maximum
!.t:'ating surface contact, mavimurn opportunity for uni-
form gasket loading, and improves the effectiveness of
all bolt tightening methods. The following guideline..,
apply for aligning mating flanges.
E-2 GUIDELINES FOR ALIGNING FLANGES
(n) Out-of-tolerance conditions should be corrected
before the gasket is installed to avoid damaging it. Only
minimum or reasonable adjustments should be made
after the gasket is installed.
(b) When aligning requires more force than can be
exerted by hand or common hand and hammer align-
ment tools such a= spud wrenches and alignment pins,
consult an engineer.
(c) Proper alignment will result in the bolts passing
through the flanges at right angles and the nuts resting
flat against the flanges prior to tightening.
(d) Before using jad.~ or wrench devices, a pipe stress
analysis mil)' be appropriate, especially if the pipe is old
or it is suspected that the willis have thinned from LIse.
(t') If the flange' that are in need of aligning are con-
nected to pumps or rotating equipment, great care must
be taken to prevent introducing a strain into the equip-
ment housing or bearing-. Measuring the movement in
the equipment to en-ure that it::. aligned condition i!)
not disturbed is a common and necessary practice. (See
"parallelism" and "rotat innal-t wo hole" under
para E-2A.)
(f) The best practice io; to repair the misaligned com-
ponent by replacing it correctly, removing and reinstall-
ing it in the properly aligned position, or using uniform
heat to relieve the stresses,
(g) In joints where one 01' more of the flanges are not
attached to piping or vessels, such as cover plates and
tube bundles, usc ample force to accomplish the best
aligned condition.
(II) Once the flanges art.' aligned, install the gasket
and tighten the fasteners completely, and then release
the aligning devices. Follow this rule as closely as possi-
ble. External forces have 11!'i-;effect on properly loaded
joints.
L F r ,.
E-2.1 Large Piping Connected to Load-Sensitive
Equipment
It is recognized that more stringent alignment toler-
nnces may be required Ior large piping connected to
load-sensittve equipment such as machinery. For
machinery,refer to API Rlo'commentied Practice 68h,
Chapter 6, Sections ".6 through 4.9 and Fig. 8-4.
E-2_2 Critically Stiff Piping System
Stringent alignment tolerance guidelines that apply
to a critically stiff piping system such as may be con-
nected to a pump or other rotating equipment nozzle
are covered in paragraph 1.2.2 of WRC Bulletin 449
(Guidelines for the Oesign and Installation of Pump
Piping Systems). This guideline ac ounts for the stiffness
of the system and is based on misalignment not causing
more than 20% of the pump nozzle allowable loading,
VVhere rotating equipment is not involved a tolerance
'* times as large may be considered.
E-2.3 Stiff or Troublesome Piping Systems
For very stiff or troublesome piping systems larger
than ON 450 (NPS 18), it may be beneficial and more
econom ica I to consider the special gu idel ines of
paragraph 1.2.3 of WRC Bulletin -149 concerning the
modification or rebuilding of a portion of the system to
assure acceptable alignment.
E-2.4 Terms and Definitions
centerline IIigll/low: the alignment of piping or vessel
flanges so that the seating surface", the inside diameter
of the bore, or the outside diameter of the flanges match
or meet with the greatest amount of contact surface.
Tolerance is usually measured by placing a straight
edge on the outside diameter of one flange and
extending it to or over the mating flange. This is clone
at four points around the flange, approximately 90 deg
from each other. The tolerance i-; 1.5 rnm (~h in.) at cd as per-
centagv-- "f T~rgo:l Torque (the torque calculated ItI produce the
finol dc,heLl IOJd or ",lInping for cc ill 1111.'joint). 1 he percentage
",llu." "ssignl.'d to theM' inll'rnlcdi.llc steps arc upP"I\imale and
not e\,l( t, .1' their purl"'''' i, to 1",""01,' .,,'NI and gr,lLiu,llnppllcn-
til'" (" I\I.IJ, and 10 ,,,,,id condition-, which ll\i~hl irrcpM.lbly
da'l'I.l);'· ., g."lo.ct. (", en the Target 'torque numbers should be
IOlllo.ed Up"" .:IS Ihe (,'nl"r nl an '"ll-pl,lblc r.mg.', and not ,"
dbMl111ll' pllinl value-. ("'CI",,, 12). 1V.lhlOleach P,.~~,inh'rolwd',llc
• )1' rill,ll, "oll,i,teney .111.1gl'old'hll,lpplkc1lion lit 1"".1 around th,~
joint i, lh,' goal 1 hl' term .. forget Torque" -houhl not 1>11 I"I-.:n I"
impl) Ih.ll the iI~wl1lbl\' 1','lIern~ Ii,l,'d here MI! .1pplil.lblt: "OIl,
10 1c",bl~ 1 he pauem- Me ,,1'0 applt-
(vb'" III utlwr mdlwd, "r joilll .,s'I·l1lbl), ~u~h d' (l'n,iun ilnd
unnllll,olll'd. A';~"IlI"ly of 1I"ngcs wilh ,1 l;:1rgc 'H""l,,'1' or bolh
will l'L'nl'lil l!'l'm """'I"'" b\Iltin!, (tIghtcning !;"llUp" (lr Ihr,'c or
tt'ur bull ...) Rd"r II) ·1.lbl~-I
Illl' Il'~For soft gaskets,' a minimum ot two pattern PJS!>E'S
are required.
For hard gaskets, I ,I minimum of one pattern 1'.155
is required.
For problematic joints, it is recommended thJt an
additional pattern Po1SS be cornplcted above the mini-
m~lm required .
F-l.2 Alternative Assembly Pattern #2
This pattern u e" a modified b()ltin~ path~1n that is
!>implC'rto fullow thill1 thl: Legacy pattern alld dlW5 lIot
rCo!qllir~the n-,sl'mbll:'r In mark the bolt nllmh~rs on the
t1ang~,!ls the next looo;e h\)lt in ,Iny gh'l:!l1qu"dr,)I1t will
ellway" be the nexl bolt 10 ti~hten. l'.ltll'rn #2A ()I I"ig. F-3
follows ,1 star paltern, wlwrea~ 1',111~rn #213npplil'-;fllilyapplied in limited applk.,tiono; ,IeWS., Ih~
51
~. I(JI'" I, II II ill! ' I
e
III
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E
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11\...
oz
ASME PCC·1-2013
-0 '"
'"0o .-.... -... .....,,
.:;:;
ro
c....
C1I....of Targel Torque (untit nuts do not turn):
1,2,3.4,5,6,7,8,9,10,11,12.13,14,15,16,17, 18.19.20.21,22.23,24 -
1,2,3. etc.
(2) 24-801t Example - Circulor Sequonco
(suitable only for >16-bolt flanges):
(a) Pass 10- 20% LO30% orTarUel TOIque: 1,7.13,19
(b) Pass 1b - 50% 10 70% of Taruet TOIque: 2,8,14.20
(c) Pass 1c - 100% of Turget Torque: 3.9.15,21 - 4,10,16,22 - 5,11,17,
23 - 6,12,18,24
(d) Pass 2 (If second pnrtern Pass specified) - 100% of Target Torque:
1,7,13,19-2,8.14,20-3,9,15,21-4,10,16,22 -5,11,17,23 -
6.12.18,24
(el Pass 3 onward - 100~o of Target Torque (until nuts do not turn):
1,2,3.4,5,6,7,8,9,10,11,12,13,14,15.16,17, 18,19.20,21,22,23,24 -
1,2,3, etc,
56
I II II ,I, I I II
ASME peC-1-20B
full rnnge of gaskets and joint configurations cornrnonly
found in rt'fining appllcations.
Ti~hlcning sequence for Pattern #2 is described in (a)
through (!.
A step-by-step example is shown in Fig. 1'-9.
(n) Pass -#1a: Proceed in the pattern outlined in Fig. F--1
and tighten four bolts, equally spaced at 90 deg apart,
III 20";', to 30% of Target Torque.
(11) Pass #1 b: Tighten the same four bolts tn 50% to
70"/', (If Target Torque.
(c) Pass 4t'1c: Tighten the same four bolts to '100% of
Target Torque,
(d) Pass #Id onward: Tighten in circular Passes at
IUO% of Target Torque until the nuts no longer turn.
F-l.4 Alternative Assembly Pattern #4: Simultaneous
Multlbolt Tightening Pattern (Group Numbering
System)
Tile simultaneous use (If multiple tools spaced e-venly
around a flange has been shown to give equal 01' even
2 " BIll11i~hl"nll1g Proccdun, for Pressure Boundary Flilngc,IJl)int
Assembly," ISA us B 2251. 20nB.
, r '" I '" j I', I" h 11 ~ ., I I
Fig. F-4 Alternative Assembly Pattern #3
(Circular Pattern)
GENERAL NOTES:
(a) Pass 1a - 20% to 30% ofTarget Torque: 1,13,7.19
(b) Pass Ib - 50% to 70% of Target Torque: 1,13,7.19
(c) Pass rc - JOO% of TargetTorque: 1,13,7.19
(d) Pass ld onward - 100% of Target Torque, in circular pattern,
until nuts do not turn. 1,2,3,4,5.6,7.8,9.10,11,12,13.14.15.
16.17.18.19,20.21.22.23,24 - 1,2,3. etc.
superior tightening parity, and parallel closure, in less
time than using a single tool in a cross-pattern (see
Fig. F-S). This method has been successfully applied in
limited applications across the full range of gaskets and
joint configurations commonly found in refining and
petrochemical applications.
As a practical matter, rnultibolt tightening works best
on larger flanges [bolt diameters M20 (~ in.) or larger],
with hydraulic tools connected to a common presslIr€
source. One tool per every four to eight bolts in the
flange should be used in even-numbered groups of tools
equally distributed around the flange. For very critical
and/or time sensitive bolting jobs, 50'1~.or even 100%
tool coverage is recommended.
NOTE: A minirnurn llf tour bolts Ml' tightencJ ~irnull''''l·I'I"ly.
F-1.4.1 Group Numbering, Number the flwith
the bolt sequence groups corresponding to the number
of bolts in the flange and the number of tools employed
(for I/lis exnmp!«, nS:HUI/(' ns ~/1UT1'11 ill Fig. F-5, 7(lill1 10111'
lOll Is lll!ill,'? IISI'd 10 lig/III'II).
(a) Mark the hoi ts at the" 2, 3, 6,11111190', luck jI()$il ions
with the number one.
(ll) Moving clockwise, split the angles bel ween the
marked bolts and number the next group as number two.
(r) Split the remaining large angles as evenly as you
can and continue numbering tho groups until ,111bolts
57
II II " I I 1 (it ( ~P I d II \\' 'I II (0, II !
ASMEPCC-1-2013
Fig_ F-5 Alternative Assembly Pattern #4
(Multi bolt Legacy Pattern)
24-BOLT FLANGE
4 TOOLS AT ONCE
are numbered. All bolts are now numbered in groups
at 90 deg from each of their own number.
F-1.4.2 Tightening. lightening is accomplished in
three Passes.
(a) Pass #la and #lb: Tighten approximately one-
fourth of the bolts to 50% of the Target Torque. In this
example, lighten all of the is and then all of the 2& to
50% of the Target Torque. It is not necessary to do the
remaining bolts because the purpose of this initial Pass
is to seat the gasket and square up the flange. Plange
alignment and gap should be checked. The remaining
bolts will have loosened so time can be saved at this
point by snugging them again.
(b) Pass #lc: Tighten all of the bolts to 100% of the
Target Torque beginning with the 35 then 4s then 55 then
6s then returning to the Is then 25.
(e) Pass #2 (check Pass): Beginning from the end of
the previous Pass at 100% of the Target Torque, move
the tools clockwise one bolt at a time until the nuts no
longer turn. This is the check Pass that compensates for
elastic interaction and brings all bolts into parity.
This same procedure is used regardless of the number
of tools. 'TI1e only exception would be 100% coverage
where tightening is done in one Pass. A modified Legacy
pattern for Passes listed above is shown in Fig. F-10.
F-l.5 Alternative Assembly Pattern #5
The following describes a simultaneous multibolt
tightening pattern with a final circular pattern with two
or more tools (refer to Fig. F-6).
(n) Pass #la: Tighten bolts equally spaced 180 deg
apart fin opposite sides of the joint to 30% of Target
Torque, then rotate tools 90 deg and Simultaneously
tighten these two bolts to 30% of Target Torque.
L [10' II I ~ ,I IJ 11
Fig. F-6 Alternative Assembly Pattern #5
(Multibolt Quadrant Pattern)
2
._._._._._._._._._l_._._._._._._._._.
GENERAL NOTES: 24·801t Example:
(a) Pass la - Simultaneously. 30% of Target Torque: 1 & 13 then
78 '"... s
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63
I ,
ASME PCC-1-2013
alternative procedures mily be developed that may be
more effective and result in better sealing performance
or less assembly effort for a given application. However,
caution should be used in accepting new assembly pro-
cedure!'. There arc, generally, two viable options for
accepting bolted joint assembly procedures that are not
listed in these guidelines.
(n) Option 1 is to use it and learn if it works by
experience.
(II) Option 2 is to test a proposed procedure in an
experimental setting and to measure certain parameters
(such as uniformity (If bolt preload, even gasket COIll-
pression, physical damage to the gaskets. flanges and
bolts, etc.) versus defined pass-fail criteria. Limitations
of applying the experimental results to facility applica-
tions and com parison to existing procedures
(section F-l) should be considered.
Option I is difficult to implement across industry
because it requires people who closely monitor their
boiling success rate and art' "bitt to d iffcrcnttatc bel ween
bolting procedure-induced f,lilure versus other Ci1LlSeS
(incorrect flange design, incorrect bolt load specification,
incorrect ~ilskl:!t selection, incorrect bolt assembly, etc.),
Successful completion of a hydrostatic test is not constd-
creel su fficient evidence 1(1 conf I'm the acceptability of an
assembly procedure. Bolting contractors rnay not have
su rficiel1t knowledge (If the long term opera ting success
of their procedure t.o be able t·o rorurnent on tlw appllca-
bility of the procedure to a given application.
Implementing il new procedure to "see if it works"
should b\i done with caution and may not be 1111 option,
,15 usually the consequences of Failure will outweigh Any
advantage. Another possibitlty to implement this option
is tu use i'1 bo lt ing contrnctors experience or other
facility's experience to prov\;;, the method works (this
often means relying 011 secondhandinformation). How-
ever, this process also requires the input of someone
knowledgeable enough to determine if the experience
in the other fdcilities will translate into yOUl' facility. The
USCI' is required to determine if his particular application
is within the limits of the procedure.
There are many facilities that are successfully using
alternative procedures developed over time and thereby
are reducing their workload considerably, but over a
limited range of gasket, flange types, and operating con-
ditions. Their experience and the applicability of the
procedure mayor may not be transferable to other facili-
ties/applications. SOLll1d engineering practice and judg-
ment should be used to determine the applicability of
a specific procedure or part of a procedure to a given
application.
F-3 RTJ AND LENS-TYPE GASKETS
RTJ and lens-type gaskets have additional considera-
tions that must be accounted for when determining the
most appropriate assembly procedure. The axial move-
ment of the flanges is Significant tor these gasket types.
In addition, they are sensitive to flang0 misalignment
either prior to or during joint assembly. Due to the large
amount of axial movement of "lie flL1n~esduring 'IS5('111-
bly, the mechanical interaction (rcductlon of neighborlru;
bolt load when a bolt is lightened) can he significant,
Therefore, it is ne,,::cSSl1ryto perf 01'1l 1 multiple potlerll
posses to t?nSlII'C uniform joint closure. and 111U Itiplc final
circular passes to ensure tlh1l the desired tNPS 12), t[\is
may mean performing fOLII' pattern passes und sh: 1)1'
more ci rcular passes, even when L'n1ployin}; an a lterua-
tive assembly procedure such as the one outlined ill
pill'manu-
facturing tolerances for standard threads, thread condi-
tion issues, new versus reused bolts and nuts, the
pre:;ence of hardened washers versus turning on the
flange face, variations in nut dimensions, and the pres-
ence of coatings and lubricants. Even if these friction
conditions [51' + 0.57735/.1.,dl + O~t'J
or more approximately (from VOl 2230) to
r F [1 ' 0"/).11]= .t .1n"+ n.58}lldz + -2-
N()Tr::
• 1).1(,,' is the torque to shckh Ihc bolt.
· 1).58}lltl~ is iI"I(' torque to overcome thread friction.
D, JJu I t f r"·'2 I~ I te l~ll\·IUt·0 n\ orcorne .icc I"IClIDn.
where
0,. =
=
d2 =
d, =
effer+ive oeal'ing d iarneter of the nut face,
mm (in.)
(tI" + "i)/2
bask pitch diameter of the thread, mm (in.)
(For metric threads. d2 = d - O.M1I5p; for inch
threads, rl2 = rl - O.64S1S/II.)
inner bearing diameter (If the nut face, rnrn (in.)
l' 'i. I /1(1 "1i ,II' r, I
tI"
F =
II =
/' =
T =
f3
I-t(l
1-'-1
outer bearing diameter of the nut face, mm (in.)
bolt preload, N (lbi
number of threads per inch, in.-l (applies to
inch threads)
pitch of the thread, rnm (For inch threads, this
is normally quoted as threads per inch, II; i.c.,
p = ] /11.)
total tightening torque, N'mm (in.-Ib)
half included angle for the threads, deS (i.e.,
30 deg for metric and Unified threads)
coefficient of friction for the nut face or bol t
head
coefficient of friction for the threads
The preload F can be determined from
where
A~
1\.
tensile stress area of the thread, 111m2(Ln.2) (see
Appendix H)
percentage utilization factor for material yield
strength (default value typically 50'Y,,; i.c.,
P .... = U.5)
minimum yield strength of the bolt material,
N/mm2 (lb/in2)
Additional information on torgue formulas and the
effect of friction factors may be found in the J--imuil.lOok
of Bolts nlld Boiled Joillts.! Chapter 3 provides detailed
formulas. Chapters] 2 and 32 provide substantial addi-
tional theoretical and experimental informution and
equations, including the more specific formula that is
shown above. This formula applies to standard 60-c1eg
thread angle ASME fastener and has the advantage of
discretely reflecting the three specific resistance coml10-
nents as provided above. The same discrete approach is
a lso used in EN 159'1-1, ISO 27509, and VOl 2230.
A simplified formula for calculating Target Torque Is
presented in Appendix K_ Long experience has shown
the "nut factor" method to be equally effective aoo;the
more complex formulas. Whilt! the nut factor method
does nor address nil of the variables that can affect the
torque-preload retationship. it produces similar and
f lilly acceptable V,1 lues for the assembly of flanp;l:.'sunder
this Guideline.
I Bickford, Illhn 1-1., and NJ'so1I', S~}'('d,cds., 19'11'. "1-1.l11db,,,,k
of Bolls and Bvllt'd joints," New 1','r", l\1,lr,'d Dekker, 1111'.
68
n hi' !, \I I,· ! \I:'tlll I
ASMEP(('1-2013
APPENDIX K
NUT FACTOR CALCULATION OF TARGET TORQUE
A common method for calculating Target Torque i..,Itmates ;.111.-,1However, it is generally Iecog-
nized that the use (If through-hardened steel washers
will improve the translation of torque input into bolt
preload by providing a smooth and low friction bearing
surface for the nu t,
Washers protect the contact surface of the flange from
damage caused by a turning nut. These are important
considerations when torquing methods (either manual
or hydraulic) are used for bolt tightening.
This Appendix specifies the procurement of through-
hardened washers for bol ted flange joints covered within
the scope of this Guideline. The Liseof surface-hardened
washers is not recommended since the soft interior mate-
rial under direct compression will flow plastically; caus-
ing washer cupping and thinni.ng with associated
reduction in preload.
M-l.2 Dimensions
The outside diameter of the washers detailed in this
Appendix was selected to enable their use on flanges
with spot Faces or back facing meeting the requirements
of standard ISO 7005-1 (Piping flanges - Part 1: Steel
flanges for industrial and general service piping sys-
tems) for metric flanges and MSS SP-9 (Spot Facing for
Bronze, Iron and Steel Flanges) for inch flanges.
TIl€' inside diameter (If these washers was selected to
enable their use under the nut. Use of these washers
under the head of a bolt may lead to interference with
the boll shank or underhead fiJlet.
M-l.3 Service Temperature (Washer Temperature)
Service temperature limits are shown in Table M-1.
Note that in operation, actual bolting temperature
may be lower than process fluid temperature.
For un insulated joints, ASME B31.3 (Process Piping)
considers flange bolting temperature to be SO'Yt, of fluid
temperature,
M-1.4 Existing Standards
Washers in accordance with ASTM F436 have been
used previously on piping flanges. However, the lise of
ASTM F436 washers may lead to interference with the
II
Table M-l Service Temperature limits
Materiat
Type
Single-Use
[Note (1)]
Reuse
INote (2)J
1
4
5
6
425°C (80001')
5400( (LOOO°F)
6so-c o.200°F)
815°( (1.500oF)
205°C (400°F)
4000C (7S0DF)
425 D( (80001')
5500( (1.025°F)
NOTES:
(1) Single-use service temperature limits are based on
replacement whenever the existing washer has been exposed
to temperature in excess of the corresponding reuse limit.
(2) Reuse service temperature limits are based on metallurgical
concerns (softening) for the washer material.
spotface /backfacing on the flanges. Also, ASTM F436
does not provide dimensions for certain nominal sizes
needed for pipe or vessel flanges. The intent of the Type 1
washer in this Appendix is to spe ify a washer of the
same general material as an A5TM F436 washer but
with revised dimensions to make them compatible with
pipe or vessel flanges.
M-l.S Previous Material
Figures 1and 2 in the originnl edition of ASME PCC-I
referenced ASME SA-5·W for the manufacture of washers
for elevated temperature. This Appendix does not con-
tinue the use of this material due to material cost and
manufacturing concerns. Disccntlnuation of the lise of
SI\-5-*0 material does not imply that this material is
technically deficient.
M-1.6 Material Application
Types] and 4 washer materials are intended for use
with steel fasteners such as Grade 21"1,4, Of 7 steel nuts
per ASME SA-194. The Type 4 washer material is ZILl
alloy steel with higher service temperature. Types 5 and
6 washer materials are intended for use with austenitic
steel fasteners such as Grade 8 austenitic steel nuts per
ASMESA-194. The Type 6 washer material is a precipita-
tion hardening stainless steel that has increased corro-
sion resistance as compared to Type 5 washer material.
M-l.? Installation
To avoid any concerns about the effect of washer mark-
ings on the performance of the washer to nut interface,
71
~I ,,'I I I I II • 'I
ASME PCC·1-2013
it is recommended that these washers be installed with
the marked face towards the tlnnge surface,
M-2 PURCHASE SPECIFICATION FOR THROUGH-
HARDENED WASHERS
M·2.l Scope
M·2.1.l This Appcnd iv cox crs the chemical,
111echanical, and dirnenxiunnl requirements for through-
hardened steel washer-, for usc with fasteners having
nourinal sizes of l4 mm to 100 nun .md I~ in. to 4 in,
1 hese washers MC intl'lIded for lise on pressure con-
raining flanges \\ ith bolt-, or :,Iut.iA·193and SA·1l)4.
M·2.1.2 fhe Iypt'~ of II .1o;lwr.. covered arc
(,,1 T\ PI" I - Carbon "Iwl
(1'1 IVPl' -+ - Low .llluy ...Ieel
(1) Typ(' 5 - M,lrtl:'l1..,ilic :.;11.'\·1
(tf) rypc 6 - Prccipit.uion h,mlt'ning steel
M-2.2 Ordering Information
Orders for w.,.;l1ers urule r thrs sp('cificatitlll sh,1I1
incl Lltll' the Iollo« 1111,;:
(1/) nominal ...lze
(/I) 1\ PI" (see pM.l M·2,1.2)
(I I quantity (number or pieces)
M·2.3 Materials and Manuracture
M·2.3.l Steelll"eci in Ilk' manufacture of Welsher"
,,11.111be produced by tlw Ulw'I-hl't1llh, basic-oxygen, III'
ell -ctric-I urnace process.
M·2.3.2 WClsh~rslip to .ind including 100 111m (.J.in.)
nom inal size shall ht' through-hardened.
M-2.3.3 Minimum h..'lllpclln~ (precipitation) tern-
peratures shall be ., ... follow ...:
(nl !-or T) PI" I, 20S C (·100 F)
(II) For Tvpe 4, 370 C (700 r)
(c) For Type 5, .J.25 C (BOO 1')
(d) For Type 6, 5500C (I ,()2'1°F)
M-2.4 Chemical Composition
Wflshcrs shall conform 10 the chemic nI composition
specified in Table 1'v1-2
I CI
M-2.S Mechanical Properties
Wah,,11bl' marked with a symbol,
or other distinguishing mark .., to identify the rnanufac-
lurer or private label distributor, .1S appropriate.
M·2.tO.2 Washers shall be marked with the type,
"I," "4," "5," or "6:' as applicable.
M·2.l0.3 All marking shall be depressed and
located on the same face of the washer,
72
ASME PCC-1-2013
Table M-2 Chemical Requirements
Composition. % [Nole (1)1
Element Type 1 Type 4 [Note (2») Type 5 [Note (3») Type 6 [Note (4»)
Phosphorus (max.)
Sulfur (max.l
0.050
0.060
0.040
0.030
NOTES:
(i) Maximum.
(2) Type 4 low·alloy steel washers shall be manufactured from SAE number 4130 or 4140 steel llsted in ASTM A829.
(3) Type 5 martensitic steel washers shall be manufactured from UN5 5/11000 steel listed ill ASME SA-240.
(4) Type 6 precipitation hardening steel washers shall be manufactured from UNS 517400 stcet listed in ASME SA·69,.
Table M-3 Dimensional Requirements
for Metric Washers
T
I.D.
_j_
T-I~
Nominal Outside Diameter, Inside Diameter, Thickness,
Size, mm0.0., rnrn 1.0., mm T, mm
14 28 15 3
16 30 17 4
20 37 21 5
24 44 25 6
27 50 28 6
30 56 31 6
33 60 34 6
36 66 37 6
39 72 42 6
42 78 45 6
45 85 {,8 6
1.8 92 52 6
52 98 56 6
56 105 62 6
64 115 70 6
70 '125 76 6
76 135 82 6
82 145 88 6
90 160 96 6
95 165 101 6
100 175 107 6
GEN[RAL NOTE: Tolerances are as noted in Table M·S.
, r 'I I' I 1\ r1, 1 I I lIJ II I'll I I' "II \.1, I I" , I
ASME PCC·1-2013
Table M-4 Dimensional Requirements for U.S. Customary Washers
T
1.0.
_l
r-I 1--
Outside Diameter,
Nominal 0.0. Inside Diameter, 1.0. Thickness, T
Size. in. mm in. mm in. 111111 in.
1/1 27.0 1.063 14.3 0.563 3.2 0.125
% 33.4 1.3'1 ~ 17.5 0.688 1.. 0 0.156
1- 38.1 1,500 20.7 0.813 4.8 0.188
'l's 43.6 1.718 23.8 0.938 5.6 0.219
1 50.0 1.968 27.0 1.063 6.4 0.250
III.! 54.8 2.156 30.2 1.188 6A 0.250
11/. 60.3 2.375 33.4 1.313 6,11 0.2S0
1% 65.9 2.593 36.S 1./138 6.4 0.250
1Vz 71.4 2.812 39.7 1.563 6.4 0.250
1% 77.8 3,062 42.9 1.688 6.4 0.250
1% 82.6 3.250 46.1 1.813 6.4 0.250
17/~ 87.3 3.438 119.2 1.938 6.4 0.250
2 93.7 3.688 54.0 2.125 6.4 0.250
2'/., 1011.8 4.125 60.3 2.375 6.4 0.250
2'/1 115.9 4.563 66.7 2.625 6.4 0.250
2'1. 127 5.000 73.0 2.875 6.4 0.250
3 138.1 5.438 79.4 3.125 6.4 0.250
31;' 149.2 5.875 85.7 3.375 6.4 0.250
3YI 160.4 6.313 92.1 3.625 6.4 0.250
3J;. 173.1 6.813 98.4 3.875 6.4 0.250
4 182.6 7.188 104.8 4.125 6.4 0250
GENERALNOTE: Tolerances are as noted in Table M·6.
74
014 f 1:1 ,M,) \ I " II II I I I ,. I I In I
ASME PCC·1-2013
Table M-5 Dimensional Tolerances for Metric Washers
1l1-16 mm 20-27 mm 30-/12 mm 1.5-76 mm 82-100 mm
Dimensional Characteristics Nominal Size Nominal Size Nominal Size Nominal Size Nominal Size
lnslde diameter. 1.0.• mm -0. +0./1 -0. +0.5 -0. +0.6 -0. +0.7 O. +0.9
Outside diameter. 0.0 .. mm -1.3. +0 -1.6. +0 -1.9. +0 -2.2... 0 -2.5 .• 0
Thickness. T, 111m to.lS .o.is iO.15 .to,'t S :to.15
Flatness. mm (max. deviation from 0.25 0.30 0.40 0.50 0.80
stnlightedge placed on cut
side)
Concentricity. FIM INote (11l. mm 0.3 0.5 0.5 O.S 0.5
(inside to outside diameters)
Burr height, mrn (max. projection 0.25 O.lIO 0.40 0.50 0.65
above adjacent washer surface)
NOTE:
(1) Full indicator movement.
Table M-6 Dimensional Tolerances for U.S. Customary Washers
 11/2 through 3 in. > 3 in.
Nominal Size Nominal Size Nominal Size Nominal Size
Dimensional Characteristics mm in. mm in. mm in. mm in.
Inside diameter. 1.0. -0 -0 -0 -0 -0 -0 -0 -0
+0.81 +0.032 +0.81 +0.032 +1.60 +0.063 +1.60 +0.063
Outside diameter, 0.0. .0.81 .0.032 .0.81 .0.032 :1.60 :1.0.063 .t1.60 to.063
Th ickness. T :0.13 .to.005 ±0.13 .0.005 .0.13 ±0.005 to. 13 .to.005
Flatness (max. deviation from 0.25 0.010 0.38 0.015 0.51 0.020 0.81 0.032
straightedge placed on cut
side)
Concentricity. FIM [Note (Ill 0.81 0.032 0.81 0.032 1.60 0.063 1.60 0.063
(inside to outside diameters)
Burr height (max. projection 0.25 0.010 0.38 oms 0.51 0.020 0.6Lt 0.G25
above adjacent washer
surface)
NOTE:
(1) Full indicator movement.
Table M-7 Sampling
Number of Pieces in Lot Number of Specimens
800 and under 1
801 to 8,000 2
8.001 to 22,000 3
Over 22,000 5
75
Id[l r , II II I , (Ii (
ASMEP((·1-2013
APPENDIX N
DEFINITIONS, COMMENTARY, AND GUIDELINES
ON THE REUSE OF BOLTS
N-1 TERMS AND DEFINITIONS
ni'"scd: any form of explicit or implicit treatment that
damages the integrity of the fastener, such as uncon-
trolled tightening, overtightening, tightening without
sufficient lubrication, or process operational extremes.
bol: wit" integra! head: threaded fastener with a fixedy'
forged head on one end and employing a nut or a drilled
and tapped hole on the other end.
vall uiitliou! integra! "cad: fully threaded fastener
employing two nuts or one nut and a drilled and
tapped hole.
CO III 111011 grtuies: materials common to the
facility /industry in satisfactory quantity and price as to
be considered the normal material to use. For example,
the refining industry common grades of threaded fasten-
ers would be SA-193 B7 bolts and SA-194 2H nuts or
SA-193 B16 bolts and SA-194In the case of bolts without integral head, it is
virtually impossible to work and rework the same
threads given the current workforce practices. '-\Then 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. A
complete change of the nuts is also a step that may
create more uniformity.
(f) When using torque devices without a measure-
ment of load or elongation, determination of the friction
condition of a fastener is difficult. However, creating
similar and fairly predictable conditions on a group of
fasteners is more practical. Starting with new threaded
fasteners and treating them aLI the same is an effective
and common way to minimize load variability from bolt
to bolt.
(g) Continuous reuse is an option when you have
adequately attended to the issues herein discussed.
(II) If an adequate bolt reuse system is used, it is
advised that the fasteners be periodically replaced based
011 the following:
(1) operational fatigue or abuse, surface and/or
integral inspections, mechanical integrity inspections,
galling, nut not running freely, difficult disassembly, OJ'
joint leakage.
(2) if one bolt in a joint is replaced, it is recom-
mended that all be replaced. If all bolts cannot be
changed, and more than one bolt is changed, space them
symmetrically around the bolt circle so that they are
surrounded by old fasteners.
f I ! ! I II I .",II i' j
(i) Tightening methods that do not apply friction
loads to the threads during the loading; process, such as
hydraulic 01' mechanical tensioning, usually do J10t have
15%)
of relaxation during the initial stages of operation, such
that the effects of operational loads in increasing the
bolt stress need not be considered (i.e., gasket relaxation
will exceed any operational bolt-load increase). In some
rare cases, this may not be the case, and the limits should
then also be checked at both the ambient and operating
bolt stress and temperatures. For most standard applica-
tions, this will not be necessary.
In addition, the methodology is for ductile materials
(strain at tensile failure in excess of 15%). For brittle
materials, the margin between the specified assembly
bolt stress and the point of component failure may be
considerably reduced and, therefore, additional safety
factors should be introduced to guard against such
failure.
The method does not consider the effect of fatigue,
creep, or environmental damage mechanisms on either
the bolt or flange. These additional mopes of failure Illay
also need 10 be considered for applications where they
are found and additional reductions in assembly bolt
stress may be required to avoid joint component failure.
0-1.3 Definitions
bolt root area, mmz (in.2)
gasket area [or/4 (Go D 2 - Gl.D.2»), mrrr'
(in2)1
I Where a gil~"~thas additional g~S"d Mea, such as a pass part i-
tiun g~sket, which may not be a~ compressed as the main OLJt~r
se~ling clement, due to [lang" rotation, then i\ reduced portion of
that area, such as half the additional area, should be added III As'
GI.Ii.r GO.D.
K ==
lib
r-:
SYIl =
5yn
Sbm,,,
Sl1nlln
Sb:-cl
Sfm.~
Sgr
5g",,, =
Sg""".n
Sgmin.S
t, =
¢I.
f!frl1.,X
Og-rn~l'"
tion and damage to existing surface finish. Avoid using
carbon steel brushes on Stel inless steel flanges.
The exception based on experience i" residual 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.
(II) Examine the gasket contact surfaces of both mat-
ing joint flanges for compl lance with recom mended sur-
face finish (see Appendix C) and for damage to surface
finish such as scratches, nick., gouge;., and bu rrs. Indica·
tions f1.lI1ni.ngr,ldially across the facing are of particular
I I
ASME PCC-1-2013
concern. Refer to Appendix 0 for guidelines covering
recommended limits on gasket contact surface irnperfec-
tions and their locations.
(I) It· is recomrnended that surface-finish compare-
tor gag;t's be available to joint assembly personnel,
(2) Report any questionable imperfections For
appropriate disposition. If weld repair of imperfections
is deemed to be required, ~t!e ASME rCC-2, Article 3.5
for repair consider.irions. Appendix C provides recorn-
mended final surface finishes.
(/1) When working with problematic or critical service
[see Note (1) of Table 3) flanges of large diameter with
leak histories or suspect fabrication, it is recommended
to check gasket contact surfaces of both [oint flanges for
flatness, both radially and circumferentially, This may be
accomplished in some cases using a machinist's straight
edge and feeler gages, bur using either 11 securely
mounted run-our Zflatness gage or field machining
equipment capable of providing accurate total indicator
rend ings is recommended. Append ix 0 provides flatness
tolerance recommendations.
If weld repair is deemed to be required to achieve the
required flatness, see ASME PCC-2, Article 3.5 for repair
considerations. Appendix C provides recommended
final surface finishes.
(c) Examine bolr' and nut threads and washer faces
of nuts for damage such as rust, corrosion, and burrs;
replace/correct any damaged components. Likewise
bolt/nut combinations for which the nuts will not turn
freely by hand past where they will come to rest after
tightening should be replaced/corrected: this includes
tapped hole threads. (See ASME PCC-2, Article 3.3,
which covers repair of damaged tapped hole threads.)
If separate washers Me scored or cupped from previous
use, replace with new through-hardened washers?
(surface-hardened washers are not suitable). The condi-
tion of previously used bolts/nuts has a large influence
on the performance of a bolted joint assembly, The Iol-
lowing guidelines relating to the reuse of bolts/nuts are
offered for consideration:
(7) When using bolts LInd nuts of common grade
as fasteners, the use of new bolts and nuts up to M30
ClI/~ in.) diameter is recommended when bolt load-
control methods such as torque or tension are deemed
necessary (see Appendix N). For larger bolt diameters,
it is recommended that the cost of cleaning, deburring,
and reconditioning be compared to the replacement cost
and considered in the a sessmenr of critical issues of
the assembly. Wilen assessing the cost, consider that
1 "Bolt" ,IS used h gt'nerally do not result in a smooth,
reconditioned surface: therefore, turning bolt threads in
a lathe is the preferred method to recondition costly
fasteners. The process will remove thread material;
therefore, the user is cautioned to ensure the tolerance
limits of ASME B1.] for the original class of fit specified
are not exceeded. Any fastener with thread dimensions
less than the minimum major diameter or the minimum
pitch diameter should be replaced.
(4) Nuts are generally replaced rather than
reconditioned.
Appendix N provides supplementary information on
the bolt reuse topic.
(d) Examine nut-bearing or washer-bearing surfaces
of flanges for coating, scores, burrs, visual evidence of
out-of-squareness (indicated by uneven wear), etc. Coat-
ings over approximately 0.13 m.m (0.005 in.) thick should
either be removed or reduced in thickness, remove all
coating for critical joints. Roughness, gouges, and pro·
trusions should be removed from these surfaces. On
severely damaged flanges, machining this area may be
requi red, in which case the mini mu rn acceptable residual
flange thickness must be considered. The use of through-
hardened, flat washers" mily be appropriate to provide
smooth and square nut-bearing surfaces.
5 ALIGNMENT OF FLANGED JOINTS
Proper alignment of all joint members is the essential
element of flange joint assembly. It results in I11Jximui11
sealing surface contact, maximum opportunity for uni-
form and design-level gasket loading, and reduced fric-
tion between the nut and the flange. Guidelines for
aligning flanged joints are provided in Appendix E.
6 INSTALLATION OF GASKET
Place J new gaskd in position after determining the
absence of (or h(1villg made correction for) unacceptable
I Fbt· washers I'rntl!ct ihe nut-contact surface of th" flange r rom
damage IIl1d provide i1 smooth and luw-Iriction lI.1rl1in!( SLld.ICC
for lh~ nuts. These JI'C imporlnn! considerations when torqu i"~
methods (either mnnual or hydraulic) cHI! used for bllit lir;htl!ninfl.
Fin! washers ~lso P romot e iru proved lo.ul eI istr'ibu t ion. S"I!
Appendix M fllr !l suttnble thrnu~ll·h",dl!"cd washer l'lI"ch,ISC
spccilication l'\"idclin.;o.
2
I" (J .... II I,' '" III II Mt ~ '11" 1"1"" .. til! ,,',. I " 1,,1 f I
ASME PCC'1-20B
Table 1M Reference Values for Calculating Target Torque Values for Low-Alloy
Steel Bolting Based on Target Prestress of 345 MPa (Root Area) (51 Units)
(See section 12 for instructions on how to adjust torque values in this table.)
Target Torque, N·m
Basic Thread Designation Noncoated Bolts [Note (1)J Coated Bolts [Notes (1), (2), and (3)]
M14·2
M16-2
M20-2.S
M24·3
M27-3
M30-3
M33·3
M36·3
M,')·3
M41·3
M45·3
M48·3
M52·3
MS6·3
M64·)
M70·3
M76·3
M82·)
M90·3
M95·3
MtOO·)
110 85
160 130
350 250
S50 lISO
800 650
1 150 900
1550 1200
2050 1600
1650 2050
3350 2SS0
4200 ) 200
5100 ) 900
6600 5000
8200 6300
12400 9400
16100 12200
20900 IS 800
26400 20000
35100 26 SOD
41600 31 SOO
48 SOD 36700
GENFRAI NOlES:
(II) lire values shown me bused on a lnrget Prestress of 31,S MPn (root arcn). Sec section 12 (Target
Torque Dctermluatlcn). Tile root areas are based 011 ccerse-rhrend series fur sizes M27 and
smaller, and 3·mm puch thread series lor slzes M30 aud larger.
(b) ruere Me mnny ways of calculating Target Torque values for boiled pressure lolnts. The basis for
the torque values in Table 1M are described in the Notes below. When condltlous vat», such as dif-
tercut bolt materials or different coatings, from those considered In thls table, refer to Appendix K.
or optionally to Appendix J. of these guidelines to compute appropriate torque values.
NOTES:
(1) The tabulated Target Torque values arc based on "working" surtaces that (omply with section I;
(Cleaning and Examination of Flangeissue is the
tlang,' fa("c outer diameter touching, which reduces the
efred ive g"sket stress,
However, it i~ also important to consider the practical-
ities inv olved with the in-field application of the speci-
fied bolt stress. I( a different assembly stress is specified
for each fl,mge in a plant. including all variations of
standard piping fl'lI1ge:., then it is unlikely, without a
signific.1nt assembly quality assurance plan, that success
\\ ill actually he improved in the field by comparison to
a simpler method. Depending on the complexity of the
jOll1t.;;in a gh en plant, a simple approach (standard bolt
stress per size aero's all standard flanges, for example)
may actually he more effective in preventing leakage
th.1I1 a more complex approach that includes consider-
ation of the integrity of aLI joint components.
1hi~Appendix outlines two approaches: the simpler
Single-assembly bolt stress approach (which is simpler
to use, but may result in damage to joint components);
and a more complex joint component-based approach
that considers the integrity of each component.
0-3 SIMPLE APPROACH
0-3.1 Required Information
In order to determine a standard assembly bolt stress
across ,III flanges, it is recommended that, as a minimum,
the target gasket stress, 5g), for a given gasket type be
considered. Further integrity issues, as outlined in the
following section on the joint component approach, may
abo be con ...ldered, as deemed nece sary,
0-3.2 Determining the Appropriate Bolt Stress
The appropriate bolt stress for a range of typical joint
configuranon« mav be determined via eg. (0-1).
A
511 ·1 = ~gr--
II,.A"
(0-1)
rhe ilver,'ge bolt stress across the joints considered
111"ythen be selected and this value can be converted
into .1 torque table using eg. (a-2M) for metric units or
L'q. (0·2) Ior U.S, Customary units.
(0-2M)
l ,I I I
I ~ = 5/0 '11-: A, cbp/l2 10-2)
An example of the type of table produced using this
method is given in Table I, which was constructed using
a bolt stress of approximately 50 ksi and a nut factor,
K, of approximately 0.20 with adjustments made based
on industry experience. If another bolt stress or nut f.1(-
tor is required, then the table Ill;}y be converted to the
new value ...using eq. (0-3), where 5u'..", T'", and K' arc
the origimll values.
(0-3)
0-4 JOINT COMPONENT APPROACH
0-4.1 Required Information
There are several values that must be known prior to
calculating the appropriate assembly bolt stress using
the [oint component approach.
(11) The maximum perrnis-ible flange rotation «(~n\3\)
at the as embly gasket stress and the gasket operating
temperature must be obtained from industry test data
or rrom the gasket manufacturer. There is presently no
standard test for determining this value; howev er, typi-
cal limits \ My from 0.3 deg for expanded PTFE gaskets
to 1.0 deg for typical graphite-filled metallic gaskets (per
flange). A suitable limit may be determined for a given
site based on calculation of the amount of rotation that
presently exists in flanges in a given service using the
gasket type in question.
(ll) The maximum permissible bolt stress (5ll",",) must
be selected by the user. This value is intended to elimi-
nate damage to the bolt or assembly equipment durin);
assembly and may vary from site to site. It is typically
in the mnge of 40% to 70'X, of ambient bolt yield stress
(see section 10).
(c) The minimum permissible bolt stress (5ll",,") I11U!.t
be selected by the user, This value is intended to provide
a lower limit such that bolting inaccuracies do not
become a ignificant portion of the specified assembly
bolt !.tr~~s, Sb"I' The value is typically in the range of
20"" to .,!on" of ambient bolt vield stress.
ed) The maximum permissible bolt stress for the
flange (5/.".,,) must be determined, based on the particu-
lar Range configuration. 1his may be found using either
elastic closed-form solutions or elastic-plastic finite ele-
ment analysis, as outlined in section 0-5. In addition,
when the limits arc being calculated, the flange rotation
at that I(Md should t [oint leakage.
(J) The maxi mum as sembly gasket stress (Sgm>\) must
be obtained from industry test data or from the gasket
manufacturer. This value is the maximum compressive
:,.tres::.at the assembly temperature, based on fuji gasket
.1I"I:'a,which the gasket can ~\ ithstand without permanent
damage (excessiv e leakage or lack of elastic recovery) to
the gasket sealing element. Any value provided should
include consideration of the effects of flange rotation
lor the type of flange being considered in increasing the
gc1sket stress locally on the outer diameter.
(s) The minimum gasket seating stress (Sgmin.S) must
be obtained from industry test data or from the gns(...et
m •mufacturer. This value is the minimum recommended
compressive stress at the assembly temperature and is
based on fuU gasket area. CI he value is the stress that
the gasket should be assembled to in order 10 obtain
adequate redistribution of ,lny filler materials and
ensure an initial seal between the gasket and the
flange faces.
(II) The minimum bel ske l operating stress (Sgmi".O)
must be obtained from industry test data or from the
gasket manufacturer. This value is the minimum recorn-
mended compressive' ;1, ·1, "f,,, ..) (0·6)
Sh'p 'i: Check if the gasket assembly searing stre-ss i...,
achieved.
(0-7)
511/' 6: Check if the g,u,kl!I operating stress is
maintained.'
C;/t',' 7: Check if the g,ls(...et ma vi m u m stress is
exceeded,
Sb,., s Sg" ,IA.\'/(Ad' )) (O-y)
SI,'1' 8: Check if the flange rotation limit is exceeded.
(O-Ill)
IF nne of the final checks (Steps 5 through 8) is
exceeded, then judgment should be used to determine
which controlling limit is more critical to integrity and,
therefore, what the selected bol t load ought to be. A
table of assembly bolt torque values can then be calcu-
lated using eq. (0-2M) or (0·2). An example table (If
assembly bolt stresses and torque values u ing this
approach is outlined in Tables 0·8 and 0·9, respectively.
0·4.3 Example Calculation
NPS 3 Class 300 Flange' Operating at Ambient
Temperature (Identical Limits Used as TIlliSI;.' in
Table 0-8) with nut factor per Table 0-'1
A" 0.3019 in.2
II" S
11"'/1,, 2.42 in.~
A~ 5.17 in.:!
4>z. = 0.75 in.
Pm.,. 750 psig (0.75 ksi)
0.7.,,~
G,n = -U9in.
1 III some cases (e.g., high 1~ll1pcr.llurc "ainless steel flanges)
till' yield str ..ngthlIl11'ing
I1I1('r,lliol1. jj, those CdSC~, the rl.1I1!\i.! limit should be reduced by
till' ratio or the yields (5/.",5,,'/ S•.,). A useful r,'lil' lor determining'
if this adjustment must be performed j, 10 compare the reduction
in yield II' the amount of rel ,n ,I lion occurruig ,111..1 if the reduction
r,1tio exceeds the relaxation, till' 2 12.70 19.05 5 0.109 0.109 0.258 0.375 0.500 0.750
6 2.77 2.77 7.11 10.97 H.27 23.12 6 0.109 0.109 0.280 0.432 0.562 0.910
8 2.77 3.76 8.18 12.70 20.62 30.10 8 0.109 0.148 0.322 0.500 0.812 1.185
10 3.40 7.80 12.70 15.09 25.40 37.49 10 0.134 0.307 0.500 0.594 1.000 1.476
12 3.96 8.38 12.70 17.48 28.58 44.47 12 0.156 0.330 0.500 0.688 1.125 1.751
14 3.96 635 12.70 19.05 31.75 14 0.156 0.250 0.500 0.750 1.250
16 419 7.92 14 27 23.83 34.93 16 0.165 0.312 0.562 0.938 1.375
18 478 9.53 20.62 26.19 44.45 18 0.188 0.375 0.812 1.031 1.750
20 4.78 9.53 20.62 32.54 44.45 20 0.188 0.375 0.812 1.281 1.750
24 5.54 14.27 24.61 38.89 52.37 24 0.218 0.562 0.969 1.531 2.062
26 7.92 12.70 23.73 35.09 26 0.312 0.500 0.934 1.382
28 7.92 12.70 25.56 37.79 28 0.312 0.500 1.006 1.488
30 6.35 15.88 27.38 40.109 30 0.250 0.625 1.078 1.594
32 7.92 15.88 29.21 43.19 32 0.312 0.625 1.150 l.700
34 7.92 15.88 31.03 1,5.89 34 0.312 0.625 1.222 1.807
36 7.92 19.05 32.86 1.8.59 36 0.312 0.750 1.291, l.913
38 9.53 17.60 34.69 51.29 38 0.375 0.693 1.366 2019
40 9.53 18.52 36.S 1 53.99 40 0.375 0.729 1.437 2.126
42 9.53 19.45 38.34 56.69 /,2 0.375 0.766 1.509 2.232
44 9.53 20.37 40.16 59.39 44 0.375 0.802 1.581 2.338
46 9.53 21.30 41.99 62.09 46 0.375 0.839 1.6S3 2.441,
48 9.53 22.23 43.81 64.79 48 0.375 0.875 1.725 2.551
ASME PCC·t-2013
Table 0-2M Bolt Stress Limit for SA-lOS Table 0-2 Bolt Stress Limit for SA-lOS
Steel Flanges Using Elastic-Plastic FEA(MPa) Steel Flanges Using Elastic-Plastic FEA(ksi)
ASME B16.5 and B16.47 Series A - Weldneck ASME B16.5 and B16.47 Series A - Weldneck
Class Class
NPS 150 300 600 900 1500 2500 NPS 150 300 600 900 1500 2500
2 579 398 579 {,34 471 1.71 2 84 58 84 63 68 08
2/'l 688 326 434 398 471 543 21/2 100 47 63 ~8 68 79
3 724 1,3/, 615 579 471 579 3 105 63 89 8[, 68 84
.4 543 615 688 434 507 507 I, 79 89 100 63 74 71,
5 5l,3 724 652 507 5/,3 5/,3 5 79 105 95 74 79 79
6 721, 579 579 579 615 579 6 105 84 84 84 89 84
8 ri« 579 615 507 579 579 B 105 84 8Y 74 8l, 84
10 579 54'3 543 507 6J5 579 10 84 79 79 74 89 84
12 724 5/,3 507 543 579 61S 12 105 79 71, 79 ij/, 89
Il, S79 434 1171 543 543 14 84 63 68 79 79
16 543 434 471 579 507 16 79 63 68 84 74
18 721, l,7l 579 543 543 18 105 68 84 79 79
20 6J5 507 507 579 507 20 89 74 74 8/, 71,
24 615 471 507 543 507 24 89 68 71, 79 7l,
26 7.53 253 362 434 26 37 37 53 b3
28 217 253 326 398 28 32 37 47 58
30 253 290 434 431, 30 37 1,2 63 63
32 217 253 398 43/, 32 32 37 58 63
34 190 290 434 398 34 28 42 63 58
36 217 253 398 434 36 32 37 58 63
38 253 579 579 543 38 37 84 8~ 79
40 217 543 615 543 40 32 79 89 79
42 253 5113 615 579 42 37 79 89 84
/14 226 579 615 543 1,4 33 84 89 79
1,6 253 615 652 543 46 37 89 95 79
48 253 507 579 579 t,8 37 74 8t, 84
83
I f 1 I r ! I. ,t I • "," II ,1 'I { , Y'
ASME PCC·1-2013
Table 0-4M Bolt Stress Limit for SA-lOS
Steel Flanges Using Elastic Closed Form Analysis
(MPa)
ASME B16.5 and B16.47 Series A - Weldneck
Class
NPS 150 300 600 900 1500 2500
2 450 310 515 332 413 447
2Y2 576 284 388 377 441 1,96
Table 0-3 Flange Rotation for SA-lOS 3 724 394 545 517 432 531
Steel Flanges loaded to Table 0-2M/0-2 4 445 561 633 417 492 454
Bolt Stress Using Elastic-Plastic FEA (deg) 5 402 724 663 468 518 501
6 541 593 630 5',3 60S 535
Class 8 724 614 657 1,63 576 557
NPS 150 300 600 900 1500 2500 10 503 639 566 1,44 627 543
12 712 607 563 494 554 594
2 0.37 0.34 0.23 0.21 0.20 0.16 14 583 454 513 526 485
2~ 0.36 0.31 0.24 0.20 0.21 0.17 16 563 398 508 532 487
3 0.23 0.32 0.26 0.26 0.22 0.16 18 614 472 594 534 521
4 0.50 0.37 0.29 0.26 0.21 0.17 20 568 451 482 545 501
5 0.56 0.33 0.29 0.28 0.20 0.17 24 479 365 450 546 481
6 0.61 0.41 0.30 0.27 0.21 0.16 26 218 242 359 /,48
8 0.46 0.45 0.31 0.28 0.21 0.17 28 193 264 354 399
10 0.70 0.43 0.34 0.30 0.21 0.17 30 228 290 447 465
12 0.74 0.48 0.35 0.34 0.22 0.16 32 173 272 396 460
14 0.68 0.48 0.39 0.33 0.24 34 160 296 463 418
16 0.83 0.48 0.39 0.34 0.23 36 207 261 404 436
18 0.88 0.51 0.41 0.33 0.24 38 211 557 623 551
20 0.87 0.580.40 0.32 0.24 40 199 536 634 532
24 0.95 0.59 0.41 0.31 0.26 42 218 581 626 585
26 0.87 0.59 0.43 0.35 44 221 676 638 570
28 0.84 0.50 0.40 0.37 46 238 724 687 563
30 0.97 0.60 0.43 0.35 48 222 524 60S 625
32 0.98 0.49 0.48 0.37
34 0.87 0.52 0.41 0.35 ASME B16.5 - Slip-On
36 0.85 0.51 0.44 0.38
38 1.09 0.51 0.39 034
Class
40 0.93 0.52 0.43 037 NPS 150 300 600 900 1500
42 1.04 0.60 0.43 0.35
l,4 0.91 0.54 0.-43 0.,5 2 724 360 572 423 413
46 1.00 0.52 0.43 0.37 2>;;' 534 321 410 377 44J
48 1.04 0.63 0.42 0.35 3 714 446 563 518
4 394 594 601 467
5 446 678 507 492
6 603 458 1,95 536
8 724 538 515 456
10 477 472 430 (,29
12 674 476 421 468
14 445 283 344 504
16 453 320 370 509
18 561 376 546 514
20 487 428 499 524
24 535 395 500 528
lIn f. 1 I I J I _ I~ I I , " ,I I , I
ASME PCC·l-l013
Table 0-4 Bolt Stress Limit for SA-105
Steel Flanges Using Elastic Closed Form Analysis
(ksi)
ASME 616.5 and 616.47 Series A - Weldneck
NPS
Class
150 300 600 900 1500
2
21/,
3
4
5
6
8
10
12
] 4
16
18
20
21,
26
28
30
32
34
36
38
40
42
44
46
48
65
83
105
65
58
78
105
73
103
84
82
89
82
69
32
28
33
25
23
30
31
29
32
32
35
31
45
41
57
81
105
86
89
93
88
66
58
69
65
53
35
38
42
40
43
38
81
78
84
98
105
76
75
56
79
92
96
91
95
82
82
71.
74
86
70
65
52
51
65
58
67
59
90
92
91
93
100
88
48
55
75
61
68
79
67
64
72
76
77
77
79
79
65
58
67
67
61
63
80
77
85
83
82
91
60
64
63
71
77
88
83
91
80
70
71
76
73
70
ASME 616.5 - Slip-On
NPS 1500
Class
150 300 600 900
2
2Yl
3
4
5
6
8
10
12
]4
16
18
20
24
105
77
103
57
65
87
105
69
98
65
66
81
71
78
52
47
65
86
98
66
78
68
69
41
46
55
62
57
83
60
82
87
74
72
75
62
61
SO
S4
79
72
73
61
55
75
68
71
78
66
62
68
73
74
75
76
77
F
Table 0-5 Flange Rotation for SA-105
Steel Flanges Loaded to Table 0-4M/0-4
Bolt Stress Using Elastic Closed Form Analysis
(deg)
ASME 616.5 and 616.47 Series A - Weldneck
2500 2500
Class
NPS 150 300 600 900 1500
65
72
77
66
73
78
81
79
86
2
2Y2
3
4
5
6
8
10
12
14
16
18
20
24
26
28
30
32
34
36
38
40
42
44
46
48
0.20
0.22
0.20
0.28
0.29
0.33
0.35
0.1.4
0.116
0.46
0.54
0.54
0.60
0.59
0.77
0.79
0.81$
0.84
0.85
0.90
0.93
0.93
0.94
0.96
0.98
0.95
0.20
0.19
0.22
0.27
0.26
0.32
0.36
0.40
0.42
0.38
0.36
0.41
039
0.37
0.55
0.56
0.58
0.58
0.57
0.56
0.71
0.71
0.71
0.71
0.71
0.71
0.15
0.17
0.19
0.19
0.20
0.24
0.28
0.27
0.32
0.35
0.36
0.34
0.33
0.34
0.42
0.43
0.42
0.43
0.43
0.43
0.48
0.48
0.48
0.48
0.48
0.48
0.13
0.11
0.15
0.17
0.18
o 16
0.18
0.17
0.21
0.24
0.23
0.26
0.24
0.26
0.33
0.33
0.34
0.34
0.34
0.34
0.35
0.35
0.36
0.36
0.36
0.36
0.09
0.09
0.12
0.14
0.14
O.IS
0.15
0.16
0.15
0.15
0.17
0.18
0.19
0.20
0.08
0.07
0.08
0.10
0.10
0.10
0.11
0.10
0.11
ASME 616.5 - Slip-On
NPS 1500
Class
150 300 600 900
60
64
2
2'12
3
4
5
6
8
10
12
14
16
18
20
24
0.34
0.35
().I,O
0.52
0.64
0.73
0.84
1.0.2
1.09
1.14
1.26
1.34
1.38
1.52
0.28
0.29
0.32
0.38
0.43
0.49
0.57
0.59
0.66
0.70
0.76
0.80
0.86
0.91
0 . .21
0.24
0.17
o.n
0.30
0.33
0.38
0.40
0.47
0.50
0.52
0.52
0.55
0.58
0.14
0.12
0.21
0.21
0.20
0.20
0.22
0.27
0.33
0.33
0.33
0.34
0.33
0.33
0.10
0.10
85
ASME PCC·1-2013
Table 0-6M Bolt Stress limit for SA-182 F304 Table 0-6 Bolt Stress Limit for SA-182 F304
Steel Flanges Using Elastic-Plastic FEA (MPa) Steel Flanges Using Elastic-Plastic FEA (ksi)
ASME 816.5 and 816.47 Series A - Weldneck ASME 816.5 and 816.47 Series A - Weldneck
Class Class
NPS 150 300 600 900 1500 2500 NPS 150 300 600 900 1500 2500
'} 434 326 471 362 362 398 2 63 47 68 S3 S3 58
2Y2 543 253 362 326 398 434 2'h 79 37 53 47 58 63
3 724 362 507 471 362 471 3 105 53 74 68 53 68
4 362 471 5/13 362 434 4310 4 53 68 79 53 63 63
5 398 615 543 398 434 43/1 5 58 89 79 58 63 63
6 543 471 471 471 471 471 6 79 68 68 68 68 68
8 579 471 507 434 471 471 8 84 68 74 63 68 68
10 434 434 434 434 507 471 10 63 63 63 63 74 68
12 471 434 434 434 471 507 12 68 63 63 63 68 74
14 434 326 362 434 434 14 63 47 53 63 63
16 362 362 362 471 434 16 53 53 S3 68 63
18 398 398 471 471 434 18 58 58 68 68 63
20 362 398 398 471 434 20 53 58 58 68 63
24 362 362 398 434 398 24 53 53 58 63 58
26 217 181 290 362 26 32 26 42 53
28 181 217 290 326 28 26 32 42 117
30 217 217 362 362 30 32 32 53 53
32 181 217 326 362 32 26 32 {17 S3
3/, 172 253 362 326 34 25 37 53 47
36 181 217 326 362 36 26 32 47 53
38 181 471 471 434 38 26 68 68 63
40 145 434 507 434 40 21 63 7'1 63
42 217 434 507 471 102 32 63 74 68
44 154 471 471 434 44 22 68 68 63
46 217 507 507 434 46 32 74 74 63
48 217 398 471 471 48 32 58 68 68
86
ASME P((-1-2013
Table 0-7 Flange Rotation for SA-182 F304
Steel Flanges loaded to Table 0-6M/0-6
Bolt Stress Using Elastic-Plastic FEA (deg)
Class
NPS 150 300 600 900 1500 2500
2 0.47 0.34 0.21 0.17 0.15 0.16
2Y] 0.40 0.29 0.20 0.20 0.24 0.13
3 0.21 0.27 0.29 0.23 0.16 0.12
I, 0.55 0.41 0.25 0.21 0.19 0.15
5 0.61 0.32 0.27 0.25 0.20 0.18
6 0.64 0.38 0.27 0.24 0.17 0.15
8 0.46 0.42 0.34 0.25 0.19 0.15
10 0.91 0.47 0.26 0.26 0.17 0.15
12 0.79 0.37 0.31 0.26 020 0.17
14 0.89 OAl 0.28 0.25 0.19
16 1.02 0.41 0.29 0.31 0.20
18 0.93 0.54 0.28 0.25 0.18
20 1.02 0.53 0.35 0.29 0.20
24 1.12 0.44 0.37 0.2/, 0.23
26 0.81 0.53 0.33 0.29
28 0.52 0.45 0.37 025
30 0.91 0.41 0.35 0.29
32 0.59 0.43 0.31 0.31
34 0.68 0.37 0.34 0.24
36 0.54 0.44 0.30 0.31
38 1.00 0.46 0.35 0.26
40 0.91 0.55 0.35 0.28
42 0.52 0.64 0.34 0.32
44 0.54 0.48 0.34 0.27
46 1.00 0.55 0.41 0.28
48 0.51 0.55 0.38 0.32
87
, ~ 1 I II I I II I ( l h._t \lll, I It II
ASME PCC·t-20B
Table 0-8 Example Bolt Stress for SA-lOS Steel Weldneck Flanges,
SA-193 B7 Steel Bolts, and Spiral-Wound Gasket With Inner Ring (ksi)
Calculated Bolt Stress (ksi)
NPS 150 300 600 900 1500 2500
2 Yl-j H U " AI 35
2'/2 'm 44· .. 410 0 35
3 ~ 63 M •• H 35
4 ~ m il5 cG A 35
5 m ~ f.t'I ·AI • 35
6 m:t ~ 14c ~ -- 35
8 m m f1;.." .. 36 35
10 m:t ~ 8t jQ 35 35
12 ~ ~ -. ... 35 35
14 ~ 63 IW 44& 35
16 o?t 63 U. .Al 35
18 ~ 68 .. M. 35
20 ~ 74 • 7 • 35
24 ~ 68 _.II 35 35
26 37 37 ,41 35
28 35 37 ~ 35
30 37 42 41 35
32 35 37 35 35
34 35 42 H, 35
36 35 37 35 35
38 37 t1 tI 35
40 35 ii! ~H 35
42 37 '1 35 35
44 35 . IB 35 35
46 37 .., 35 35
48 37 ja 35 35
_ m limited by mill. bolt stress
_ .. limited by max. boll stress
_ .. limited by max. gasket stress
_ .. limited by max. flange stress
Example Limits Used in Analysis:
5bm,n .. 35 ksi
se;.... 75 ksi
5fm••.. from Table 0-2
5g! .. 30 ksi
59m •• " 40 ksi
5gm,n.S" 12.5ksi
5gmin•O = 6 ksi
egm .. = 1.0deg
88
I~ I I, 'II'
ASME PCC·1-20t3
Table 0·9 Example Assembly Bolt Torque for SA-lOS Steel Weldneclby providing
(a) an investigative and diagnostic evaluation guide
to c.ha ract e riz e the [oint in terms of its h istorica l,
operating, and mechnnical status
(/I) a sam pic" FISLlre surge, and thermal
loadings may occur and affect the gasket load and joint
tightness.
P-4.1.1 External Bending or Axial Force
(a) Review design docu merits and calcu latioi IS for nny
specified additional forces and compare these with cur-
rent operating circumstances. Consider the reactions of
piping systems against nozzles and vessel joints,
(1J) Review against design documents the actual pip-
ing system layout, support, guides, and constraints for
sources of unanticipated bending or axial forces. Con-
sider the effect of unintended restraint of pipLng thermal
expansion in terms of forces and bending moments.
(c) Evaluate the effect of external loads on the joint.
Reference ['I] and its references provide methodology
for the eva Illation of external loadings on pressurized
flanged joints. Public computer programs exist that are
fully capable of evaluating external loadings on flanged
joints,
(d) Although not specifically referenced in
Appendix 2 of Section VIJ I, Division I of U1e Boi ler and
Pressure Vessel Code, the requirement that all loads be
considered is covered i.n Code para. UG-22 Which, if
considered, will diminish the likelihoodof leakage,
P·4.1.2 Differential Thermal Expansion (OTE). Differ-
ential thermal expansion between the bolts and flanges
is present in(1[ carbon or low-alloy steel flanges to
solid high-nlloy shells to design temperatures no higher
than 232°C (450~~), 1I111 subject to moderate corrosion
such as 10 require" corrosion allowance in excess (If
1.5111III (Yt" in.); consider face-weld lea kage and resut tel nt
hidden corrosion ill crevice between tlnnge 1.0. ,Ind
shell.
(5) avoid use in hot hydrogen service [defined for
carbon steel as a hydrogen partial pressure exceeding
lOO psia with a corresponding coincident temperature
exceeding 200°C (400oP)l, or other suitable company- or
industry-defined hydrogen service limits.
P-4.6.3 lap Joint Flange (See Fig. P-3)
(n) Allows lise of high strength, carbon, or low-alloy
steel flange material in services where expensive
high-alloy pressure-boundary materials are required.
(b) Allows use of closely matching coefficients of
expansion of flange materials as described above with
high-strength bolting such as SA-J93-B7, SA-193-B'16,
SB-637 (Alloy N07718), etc.
(c) Superior flange style when the joint 'due to excessive
initial gasket creep during
heat-up
Loss of bolt load due to
excessive transient
differential component
temperature
Improper assembly
Some bolts galled or galling
under nuts
Improper pipe support or
restraint causing excessive
bending moment
Gasket shifted off flange face
(not centered)
Gasket unevenly loaded
Poor gasket selection or
design
(a) Increase initial bolt load. See Appendix 2 of Section VIII,
Division 1.
(b) Consider hot torque (if safe) during warm-up.
(c) Increase joint flexibility by increasing effective bolt length
(see para. 8.2.1) considering boll extension collars or con-
leal spring washers that are clearly identified as such.
(d) Use gasket with reduced relaxation properties.
(a) Increase assembly bolt load.
(b) Increase gasket width.
(c) Increase joint flexibility by increasing effective bolt length
(see para. 8.2.1) considering boll extension collars or con-
ical spring washers that are clearly identified as such.
(d) Perform thermal-structural analysis to evaluate transient
flange/bolt deformations as means to discover further
remedial actions.
(e) Consider replacing flanges with lap-type flanges as a
means to reduce flange bolt differential expansion.
See same item in LHT
See same item in LHT
(a) Check support, restraint system against design.
(b) Analyze as installed piping system thermal and weight
response with emphasis on bending moment at flanged
joints.
Cc) Correct any deficiencies.
See same item in LHT
See same item in lHT
(a) Consider inner gage ring.
(b) Use another. less soft. gasket style.
(c) Consider buckle-resistant gasket type.
97
I II 11 It, I II
AS ME PCC-1-2013
Telltale Signs
Table P-3 leak Corresponding to Thermal or Pressure Upset (lCU)
Potential SolutionsPossible Cause
Leakage stops or reduces
once operation returns
to steady state
Leakage corresponds to
external event and
generally stops on
return to steady state
loss of bolt load due to
process thermal (or
pressure) transients
tal Increase gasket width.
(b) Increase assembly bolt load.
(c) Increase joint flexibility by increasing effective bolt length (see para. 8.2.1)
considering bolt extension collars or conical spring washers that are clearly
identified as such.
(d) Consider operational changes that slow heat or cool rates, or reduce
thermal swings.
(e) Consider replacing flanges with lap-type flanges.
(a) Increase assembly bolt load.
(b) Consider external shielding.
Sudden environmental
change such as rain
deluge
Telltale Signs
Table P-4 leak After long Term (Months) of Operation (lTO)
Potential SolutionsPossible Cause
Gasket structure/filler missing or
no longer flexible or compliant
Spring hangers incorrect, support
lift·ofr, incorrectly placed
restraints
Bolts are not tight on inspection
Bolts not tight on inspection.
obvious gasket deterioration,
gasket structure no longer
sound
Gasket structure no longer sound
(double jacket broken or wind-
ings buckled), marks on gas-
ket surface corrcspondlng to
radial flange face movement
Gasket chemical degradation
(chemical decomposition,
oxidation, etc.)
Improper pipe support or
restraint
Change gasket type.
See same item in 1.10.
Bolt load loss due to long
term gasket creep
Physical gasket degradation,
gasket unsuitable for
operating temperature
See same item in UO.
Replace gasket with a type suitable for operating condl-
tions.
Gasket physical degradation
due to flange differential
radial movement
(a) Remove all flange face nubbins.
(b) Replace gasket with a type capable of taking radial
shear and greater abrasion such as the First three
types listed in Appendix C.
98
U·, I ,I h" (II II (III ,'1" I" II I , 11 I
ASME PCC-1-2013
Possible Cause
leak During Shutdown (lOS)
Potential Solutions
Table P-5
Telltale Signs
Bolls are not tight on inspection
Bolts not tight on inspection,
obvious gasket deterioration,
gasket structure no longer
sound
Bolls not tight on inspection,
obvious gasket deterioration,
gasket structure no longer
sound (double jacket broken
or windings buckled), marks
on gasket surface correspond-
ing to radial nange face
movement
Bolt load loss due to long
term gasket creep together
with differential compo-
nent cooling
Physical gasket degradation,
gasket unsuitable for
operating temperature
Physical gasket degradation
and loss of bolt load due
to flange differential radial
movement
(a) Increase initial bolt load.
(b) Consider hOI torque (if safe).
(e) Consider different gasket type more suitable for
operating conditions.
Replace gasket with a type suitable for operating
conditions.
(a) Remove any flange face nubbins.
(b) Replace gasket with a type capable of taking radial
shear such as (he first three types listed In
Appendix C.
L)9
, I J II I
I •
INTENTIONALLY LEFT BLANK
fl, 11, I I ,,~II} ,~t
'100
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writing to the stafr secretary. Additional procedures for inquiries may be listed within.
, I II I I II ,~I I I I II\ Iand Fastener Contact Surfaces) and sectton 7 (lubrication of
"Working" Surfaces). The Target Torque values were computed using nut faltors selected to achieve
a Target Prestress of 345 MPa. The torques were adjusted based on industry experience and veri-
Ired by boil elongation measurements.
(2) The coating on coated bolts is polyimide/amide and rs considered to be the sole source of
"working" surface lubrication; the application of a lubricant 10 the coated surtaces can result in a
considerable reduction in the assumed coefficient of friction of approximately 0.12. (See
Allpendix K for equivalent nut factor.)
(Jl Coated torque values apply only for initial tightening of new. coated bolts using the torque-
increment rounds shown in Table 2. For second and subsequent tightening by torquing methods.
use of lubricants and torque values as specified for noncoated bolts is recommended.
3
l. , I, • I , , , ,(1 I .. I -!,
ASME PCC·1-2013
Table 1 Reference Values for Calculating Target Torque Values for Low-Alloy
Steel Bolting Based on Target Prestress of 50 ksi (Root Area)
(U.S. Customary Units)
(See section 12 (or instructions 0/1 how to adjust torque valLies in this table.)
Target Torque, ft-lb
Nominal Bolt Size, in. Noncoated Bolls [Note (1)] Coated Bolls [Noles (1). (2), and (3)]
60 liS
120 90
210 160
350 250
500 400
750 550
1.050 800
1,400 1,050
1,800 1,1,00
2,350 1,800
2,950 2,300
3,650 2,800
4.500 30400
6,500 4.900
9.000 6.800
12.000 9.100
15.700 11,900
20,100 15,300
25.300 19.100
31,200 23.600
38,000 28,800
GENERAL NOTES;
(a) The values shown are based on a Target Prestress of SO ksi (root area). See section 12 (Target
Torque Determination). The root areas are based on coarse-thread series for sizes 1 in. and
smaller. arid 8-pitch thread series for sizes 11'8 in. and larger.
(b) There are many ways of calculating Target Torque values for bolted pressure joints. The basis for
the torque values in Table 1 are described in the Notes below. When conditions vary. such as dif-
ferent 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.
NOTES:
(1) The tabulated Target Torque values are based on "working" surfaces that comply with section 4
(Clenning and Examination of Flange and fastener Contact Surfaces) and section 7 (Lubrication of
"Working" Surfaces). The Target Torque values were computed using nut factors selected to achieve
a Target Prestress of SO ksi. The torques were adjusted based on industry experience and verified
by bolt elongation measurements.
(2) The coating on coaled bolts is polyimidejamide and is considered to be the sale source of
"working" surface lubrication; tile application of a lubricant to the coated surfaces can result in a
considerable reduction in the assumed coefficient of friction of approximately 0.12. {See
Appendix K for equivalent nut factor.}
(3) Coated torque values ~pply only for initial tightening of new. coated bolts using the torque-
lncrernen; rounds shown in Table 2. For second and subsequent lightening by torquing methods.
use of lubricants and torque values as speCified for noncoated bolts is recommended.
4-
III1I ~1 ,I , 1 II II t
ASME PCC-1-2013
gasket ~e,'ling surface imperfections and flatness toler-
ance deviations. as well as joint alignment considera-
tions (st't' Appendices 0 and E).
Reust' of 11 gasket is not recommended. However, the
substrates of grooved metal gaskets with facing layers
may be reused after having been reconditioned and
ref11 ilable
for the expected runge of service ternperaturets) ,111"
antiseize requ irernents.
(c) Before lubricant is applied to the bolt and nut
threads, nuts must run freely by hand past where they
will come to rest after tightening. If nuts will nut turn
freely by hand, check for cause and make neces ...arv
correctionc/ replacements.
(d) For noncoated bolts (see NOles to Table 1M/
Table n apply lubricant liberally and completely to the
nut contact faces and to the threads on both ends of
the bolls past where the nuts will come to rest after
tightening; the lubricant should be applied after the
bolts are inserted through the flange bolt holes to avoid
possible contamination with solid particles that could
create unwanted reaction torque. Lubrication should be
applied irrespective of the tightening method used.
(e) For new coated bolts and nuts (see Notes 1'0
Table IM/1~')blC']), free-running nut checks as described
in (c) are required. On the second and subsequent tight-
ening operations, apply lubricant as described in (d).
(1) The reference torque values for new, coated
bolt /nuts shown in Table 1M/Table I do not consider
lubrication other than that provided by the boll/nut
coating [see Note (2) of Table 11',,1/ lable II. When rell~ing
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).
if) While it is recognized that the i.nherent lubricity
of new coated bolts results in less torque being required
during the first tightening operation to achieve a gh en
level of tension in the bolt (sec Table 1M/Tablc 1), the
major long-term value of coated bolts is to protect
against corrosion of the exposed threads and to mini-
mizebreak-out and nut-removal torque, thereby pro-
moti.ng ease of joint di assembly [see section 15, and
Note (3) of fable 1M/Table 1].
(g) Do not apply either approved lubricant or unap-
proved compounds to the gasket or gasket-contact sur-
faces; protect against inadvertent application to these
surfaces.
8 INSTALLATION OF BOLTS
Install bolts and nuts so thev are hand-tight with the
marked ends of the bolts and nuts located on the same
side of the joint and facing outward to facilitate inspec-
tion; then snug lip to 15 Nrn (JO (t-Ib) to 30 N-m (20 ft-lb),
but not to exceed 20'y', of the Target Torque (see se lion
12). If nuts do not hand tighten, check for cause ,1111.1
make necessary corrections.
8_1 Bolt/Nut Specifications
Verify compliance with bolt and nut specifications
[materials, diameter, length of bolls, thread pitch, and
ASME PCC-1-2013
nut thickness equal to the nominal bolt diameter (heavy
hex series nutsl].
8_2 Bolt lengths
Check bolts for adequate length. This length should
consider the presence of washers, nut height, and
required thread protrusion, Section VIll, Division 1 of
the ASME Boiler and Pressure vessel Code requires that
nuts engage the threads for tilt' full depth of the nut (see
para, UG-13). The ASME B31.3, Process Piping Code, has
a similar provision but considers the nut to be acceptably
engaged if the lack of complete cllgaljement is not more
than one thread (see pMJ. 335.2.3). The use of bolt ten-
sinners requires that the threaded portion of the bolt
extend at least one bolt diameter beyond the outside
nut lace on the tensioner side of the joint. Galvanized or
coated bolts may requirt' ;!..l'lcreep, embedment lossos, rind joint hear-up. TIll'
..,('l,.;itivity Lo this occurrence should be given c.uvful
•1ttcnrion along with other joi lit considerations when
l-i1'11>l'tin);tlw level of TilI'!-\('tBoll Stress,
9 NUMBERING OF BOLTS
9.1 Numbering of Bolts When a Single Tool Is Used
When either the I cg.1L), ()J' t-.lodified r egacy method-,
an' used, the corresponding bolt-numbering systems art'
.1... follows:
to) A system whereby each bolt location, starting with
number 1 and continuing lhrough N, is numbered
sequentially on the Fi.lngt: in a clockwise manner (when)
N is the total number (If bolts in the joint). This system
W,IS used in ASME I'CC-I-2000. It has been retained
(and therefore referenced ,I,> lhe Legacy method). The
cross-pattern passes are completed using the pattern
outlined in Table 4, Leg,)Cy Crlls~·Pattern TIghtening
Sequence and Bolt- lumbering S)'~tem. This numbering
~ystem allows, for example, Ihe quick identification of
I, A bolt having an CflCtlll'C Imglh ~hortcr Lhan 5 times its nomindl
di,1mclcr is generally con~ill~""d lo be "short."
holt number 20 in a .jO-bolt 1'1,1I11;;t'but requireslosses. If the flange is subjected 10 a subsequent test pressure higher than its rating, it may be
desirable to repeat this round after the test is completed.
Table 3 Recommended Tool, Tightening Method, and load-Control Technique Selection
Based on Service Applications
(See para. 1O.1)
Service Applicalions
[Note (l)J Load-Control TechniqueTools [Note (2)] Tightening Method
Mild Service
Intermediate Service
Critical Service
Manual or auxiliary-powered tools Pattern single or multi bolt
tightening procedures
Consistent procedures per
industry best practices or
torque control
Sec Note (3)Manual or auxiliary-powered tools
or torque- or tension-measuring
tools
Pattern single or multibolt
tightening procedures
Torque- or tension-measuring
tools
Pattern Single or multibolt
tightening procedures
Torque or tension control with
final bolt elongation/load
verification optional (Note (4)(
NOTES:
(1) Service Applications should be designated by the user and should consider governing design conditions (pressure, temperature, etc.),
mechanical criteria (bolt diameter, flange diameter, gasket type, etc.), joint leakage history, and fluid service category.
(0) An example of Mild Service could include Category D Fluid Service as defined in ASME 831.3.
(b) An example of Intermediate Service could include Normal Fluid Service as defined in ASME 831.3_
(c) Examples of Critical Service could include service requirements as defined by local jurisdictional rcquirements (example for
United States is CFR 1910.119 (OSHA PSM rule)]. lethal substance service as defined in the ASME Section VIII, Division 1 Code, or
Category M Fluid Service as defined in ASME 831.3.
(2) All tools are to be regularly and properly maintained and calibrated.
(3) It is recognized that many joints are regularly tightened using impact wrenches or manual tools with no precise load control. Experi-
ence may prove this is sufficient for certain applications, but unmeasured tightening is not recommended for intermediate service appli-
cations without careful consideration of the risks.
(4) Where past practice with specific or similar equipment warrant or where testing/research validates, elongation and load verification
may be waived.
7
ta. d I., Fr r.' F ~I II IJ .. D ~.", d~d t1 .;11 1 I I ~ AU :: 11 , li ,I
ASME PCC-1-2013
Table 4 legacy Cross-Pattern Tightening Sequence and Bolt-Numbering System
When Using a Single Tool
No. of
Bolls Tighlening Sequence for Cross-Pattern Passes [Note (1)J
4 1·3·2·4
8 1-5-3-7 _, 2·6·4·8
12 1·7·4·10 _. 2·8·5·11 -) 3·9·6·12
16 1·9-5-13 .... 3·11·7·15 _. 2·10·6·14 _, 4·12·8·16
20 1-11-6-16 _, 3-13-8-18 -) 5·15-10-20 -) 2·12·7·17 -) 4-1/,-9.19
24 1·13-7-19 _, 4-16·10·22 ... 2·14·8·20 _, 5·17·11-23 -) 3·15·9·21 _, 6·18·12·24
28 1-15-8-22 _, 4-18·11-25 _, 6·20-13·27 _, 2-16·9·23 _, 5·19·)2·26 _, 7·21·14·28..J
3·17·10·24
32 1-17-9-25 _, 5-21-13·29 .... 3·19·11·27 -) 7·23·15·31 _, 2-18·10·26 _, 6·22·14·30 J
4-20-) 2-28 -+ 8·24-16-32
36 1-2-3 _, 19-20-21 _, 10-11-12 _. 28-29-30 _, 4-5-6 _, 22-23-24 _, 13-14-15..J
31-32·33 _, 7·8·9 .... 25·26·27 _, 16·17·18 -) 34-35·36
40 1·2·3·4 _, 21·22·23·24 _, 13·14·15-16 _, 33·34- 35- 36 _, 5-6-7-8 _, 25-26-27-28 J
17-18-19-20 _, 37·38·39·40 _, 9·10·11·12 _, 29·30·31-32
44 1-2-)·4 _, 25-26-27-28 _, 13-14-15-16 -) 37-38-39-40 _, 5-6-7-8 -) 29-30-31-32..J
17·18·19·20 _, 41-42·43·44 .... 9·10·11·12 _, 33·34·35·36 _, 21·22-23-24
48 1·2·3·4 _, 25·26·27·28 -) 13·14·15·16 _, 37·38·39·40 _, 5·6·7·8 _, 29·30-31·32 J
17-18-19-20 _, 4l-42A3-44 _, 9'10-11-12 _, 33-34-35-36 _, 21·22-23-24 _, 1,5-46-47'48
52 1·2·3·4 _, 29·30·31·32 -) 13·14·15·16 _, t,I·42·43·44 _, 5·6·7·8 _, 33·34·35·36,J
17·18·19·20 _, 45-46-47-48 -) 21-22-23-24 _, 49-50·51·52 -) 25-26-27·28.J
9-10·11·12 -; 37'38-39'40
56 )·2·3·4 _, 29·30·31·32 -> 13·14·15·16 _, 41-42·43-44 _, 21-22·23·24 _, 49-50-51-52 _I
9·10·11-12 -> 37·38·39·40 _, 25·26-27-28 _, 53-54-55-56 -\ 17-18-19-20.J
45·46·47-48 -) 5-6-7-8 _, 33·34·35-36
60 1·2-3-4 -. 29·30·31·32 -. 45.46.1,7.48 -. 13'14'15-16 ~ 5·6-7·8 -> 37-38-39-40 .J
21·22-23·24 _, 53-54·55-56 -) 9-10-11-12 ~ 33-34-35-36 _, 49·50·51·52 _, 17·18·19·20 J
41·42·1,3·44 _, 57- 58- 59-60 _, 25-26-27·28
64 1·2·3·4 -> 33·31,·35·36 -) 17·18·19·20 _, 49-50-51-52 _, 9-10·11-12 -) 41-42·43-44.J
25·26·27·28 -> 57·58-59-60 -> 5·6-7-8 _, 37-38'39·40 _, 21·22·23·24 ~ 53·54·55·56 .J
13-14-15-16 __, 45·46·47·48 __, 29· 30· 31-32 _, 61-62-63·64
68 1·2-3-4 -) 37-38-39·40 -) 21·22·23·24 _, 53·54·55·56 _, 9'10'11-12 _, 45·46-47·48.J
29·30·31-32 _, 61-62·63·64 _, 17·18'19-20 _, 57-58·59·60 -+ 33·34·35·36 -+ 5·6·7·8..J
111·42·43·44 -> 13-14-15-16 -) 49·50·51·52 ._, 25·26·27·28 -) 65·66·67·68
GENERAL NOTES:
(a) See Table 4.1 covering an alternative to the Legacy pauern numbering system.
(b) See Appendix F for Alternative #1 (Modified Legacy), which uses the same numbering system as the Legacy method (Table t, or
Table 4.1) but a different torque increment than that in Table 2. Alternatives 112 and 113 from Appendix F use both a ditrerent pattern
than that in Table 4 or Table 4.1 and a different torque increment than that in Table 2. Compliance with the limitations of the apptlca-
tion of these alternatives is essential.
(c) See Appendix F for Alternatives 114and #S for alternauvc group numbering and tightening sequence when simultaneously using
multlple tools.
NOTE:
(1) See Figs. 3 and 4 for illustrations or legacy cross-pattern tightening sequences and bolt-numbering system when using a single toot.
R
,. H1!h F \H. (J , I" I I, '" I I 1 I t l 11,1. \) II I III/
ASME PCC-I-20B
Table 4.1 Alternative to Legacy Cross-Pattern Tightening Sequence and Bolt-Numbering System
When Using a Single Tool
(See section 9)
No. of
Bolts Bolt-Numbering Sequence to Be Marked Clockwise on Flange [Note (1)]
4 1,3.2.4
8 1, 5, 3. 7. 2. 6, 4, 8
12 1.9, S. 3, 11, 7, 2, 10.6.4.12.8
16 1.9. S. 13, 3. l1, 7, 15,2, 10,6,14.4. 12.8. 16
20 1.17.9.5,13,3,19.11.7.15,2,18,10.6,14.4,20.12.8.16
24 1,17.9. S, 13, 21. 3. 19.11,7,15,23.2,18.10.6.14.22.4.20,12.8.16.24
28 1.25.17.9.5.13.21,3,27,19,11.7.15.23,2,26.18,10.6. 14. 22, 4, 28. 20. 12. 8. 16. 24
32 1.25.17.9.5.13.21,29.3.27.19.11.7.15.23,31.2.26.18. 10. 6. 14, 22. 30.4.28.20,12.8.16.24.32
36 1.33.25.17.9.5,13,21.29.3.35.27.19,11,7,15.23.31,2, 34, 26. 18. 10, 6, 14. 22, 30. 4. 36,28.20.12.8.
16. 24, 32
40 1.33,25.17.9,5,13.21.29,37.3.35.27.19.11.7.15.23, 31.39.2. 3i,. 26.18,10.6,14.22.30.38. I" 36.28.
20.12.8.16.24,32. i,O
44 1.41. 33, 25. 17.9.5.13.21,29,37,3, i,3. 35. 27,19.11.7,15,23.3'1.39,2.42,34. 26. 18, 10.6. 14. 2~. 30, 38.
ft. 44. 36.28.20.12.8.16.24,32.40
48 1.41.33.25.17.9.5.13.21.29.37.45.3.43.35,27.19.11. 7. 15. 23. 31, 39. 47, 2. 42. 34. 26. 18. 10.6.14.22.
30. 38. 46. 4. 44. 36. 28. 20, 12. 8, 16. 24. 32, 40. l,8
52 1.49.41.33.25.17.9.5.13.21.29.37,45,3,51,43.35.27. 19.11.7.15.23.31,39.47.2.50. /,2, 34. 26. 18. 10.
6. 14. 22. 30, 36. 46. ". 52, t,,,. 36. 28. 20. 12. 8. 16. 2/,. 32. 40, ',8
56 I. 49. 41. 33,25,17,9.5,13.21. 29. 37. 1,5. 53. 3. 51. 43. 35, 27.19.11.7.15.23.31,39.47. 55,~. 50. 1,2. 3',. 26.
16. 10.6. 14. 22. 30. 38.46.54. I,. 52, 44. 36. 28. 20. 12. 8. 16. 24.32.40.46. S6
60 1.57,49.41. l3, 25. 17. 9. 5. 13, 21. 29.37.45.53.3.59,51.43.35.27,19.11.7.15.23.31,39. /,7.55.2,58.50.
1,2.34.26.18.10.6.14.22. 30. 38.46.54. '" 60.52,44.36.28.20.12.8. 16.2/,.32,40.48, ss
64 1.57.49./11.33.25.17.9.5.13.21.29.37./,5.53.61.3.59. 51. 43. 35, 27. 19.11.7.15.23.31.39./,7.55.63.2.
58. 50.42.3/,.26, 18. 10. 6. 14.22.30.38.46. 54.62.4.60, 52. 44. 36. 26. 20. 12, 8, 16. 24. 32. 40, 48. 56. 66
68 1.65.57, 4Y. 41.33.25,17.9.5,13.21.29.37. l,S. 53. 61.3.67.59,51.43. 3S. 27, 19, 11. 7. 15,23.31.39./,7, SS.
63. 2.66.56. 50.42. 34. 26. 18. 10. 6. 14. 22. 30, 38./,6. 54, 62, 4. 68. 60. 52. 1,4. 36. 28. 20. 12.8. 16.2/,.32.40.
48. 56. 64
72 1.65.57.49.41.33.25.17.9.5.13.21.29.37,/,5.53.61, 69. 3,67.59.51./,3.35.27.19.11, 7.15,23. 31.39.47.
55.63,71.2,66.58. 50. t,2. 34. 26. 18.10,6, 1-/j, 22. 30. 38. 46. 54. 62. 70. i,. 68. 60. 52. 1,4,36. 28. 20. 12,8. 16.
24. 32. 40, 48. 56. 64. 72
76 1.73.65,57.49. l,l. 33. 25. 17.9.5.13.21.29.37.45.53,61,69.3.75.67.59.51./13. 35. 27,19.1), 7.15.23.31.
39.47. 55. 63. 71, 2. 74. 66. 58. SO. 42. 34, 26. 18. 10.6. 14.22.30. 38.46. 54.62.70.4. 76, 68. 60. 52. 44. 36. 28,
20. 12. 6. 'J 6. 24. 32. «o, 48. 56. 64. 72
80 1.73,65.57.49.44.33. 25. 17. 9. 5. 13. 21. 29. 37. 45. 53, 61. 69. 77. 3. 75. 67. 59. 51. l,3. 35. 27. 19. 11. 7. J 5.23.
31.39.47. 55. 63. 71.79. 2. 74.66. 58. 50.42.34. 26. 18. 10.6.14. 22. 30. 38, 46. 54. 62, 70. 78. 4. 76. 68. 60. 52.
4/1.36.28. 20. 12.8. 16, 24. 32.40.48, 56. 6/" 72, 80
84 1.81. 73.65. 57.49.44.33. 25. 17. 9, 5. 13, 21. 29. 37. 45. 53. 61. 69. 77.3.83. 75.67. 59. 51. 43. 35. 27. lY. 11. 7.
15, 23, 31. 39. t,7. 55. 63. 71. 79. 2. 82. 74. 66. 58. 50. 42. 34. 26. 18. 10.6.14.22. 30.38.46.54.62.70. 78. 4. 84.
76. 68. 60. 52. 44, 36. 28. 20. 12. 8. 16, 24. 32. 40. 48. 56, 64. 72. 80
88 1.81.73.65.57,49.44.33. 25. 17.9. 5. 13. 21. 29. 37. 45. 53. 61. 69. 77.85.3.83.75.67.59.51. /,3. 35. 27. 19.11.
7,15.23.31.39, i,7. 55. 63.71.79.87.2.82.74.66.58,50.42.34.26.18,10.6.14. 22.30.38.46.54,62.70.78.
86. 4, 84. 76. 68. 60. 52. 44. 36. 28. 20. 12. 8. 16. 24. 32, 40. 48. 56. 64. 72. 80. 88
NOTE:
(1) The number assigned at each bolt location represents the sequential order for tightening the bolt.
9
ASME PCC-I-20t3
yield strength o( the bolt material (see also para. 8.2.2
regarding the effect of short bolts on the determination
of the Target Torque value), This range is normally only
exceeded in exceptional cases that have been assessed
by 11 qualified engineer. However, any maximum Target
Bolt Prestress must be selected to ensure that all three
of the joi n t com ponen ts - bo Its, flange, and gas ket - are
stressed within acceptable limits. (See also para. 0-1.2.)
Section 12 provides guidance on the determination of
the assembly Target Torque value.
Appendix 0 outlines a method to determine the
assembly bolt stress for a given flange joint (bolt, flange,
gasket assembly). The method is based on a formula and
flange stress limits that are supported by and consistent
with elastic-plastic FEA work. A calculation is provided
that uses an exaruple-specific maximum allowable gas-
ket stress; however, th.: USer must provide this inforrna-
tion. Tables Ior maximum bolt load limits are provided
f(lr ASME B 16.5/B 16.47 Series A flanges and the method
to calculate the assembly bolt load for other standard
and nonstandard flanges is outl ined.
10_1 Tightening Method/load-Control Technique
(II) Several tightellillg methods are available such as
hand wrench,slug/hand wrench, impact wrench, torque
tools, and tension tools. Also, several load-control tech-
niques art' available. Thus, several combinations of spe-
cific joint assembly methods/techniques are available
for consideration.
(/I) Four such combinations that are commonly used
are listed as follows in ascending order of bolt-load
control accu_racy; however, the implied bolt-load control
accuracy is dependent on assembly procedures, specific
material properties, a n d operator training and
competency:
(1) tightening with hand (II' impact wrenches. Hand
wrenches are practical only for bolts approximately
25 mill (I in.) in diameter and smaller.
(2) tightening with hand-operated or auxiliary-
powered tools with torque measurement.
Hand-operated torque wr ..nchos are practical only for
bolts with assembly torque less than approximately
700 N'm (500 ft-Ib).
(3) tightening with tensioning tools that apply an
Cl>-ialload to the bolt with force measurement.
(4) any tightening method used with bolt elcnga-
bon (stretch) or load-control measurement. Bolt materi-
als and properties vtlr)' within bolt types and this must
be accounted for when using these methods.
(c) The selection of the tightening method/
load-control technique for the joint under consideration
should be made based on past experience with similar
joints and full consideration of the risks (safety, environ-
mental, financial) associated with potential leaks for the
service conditions under consideration. For example, it
is widely recognized that the most accurate bolt preload
control method (± lOr;;':l or less) is d ired rneasu rement ul
residual bolt elongation (stretch) after tightening (see
para. ]0.2), whereas large bolt load variations are possi-
ble when any tightening method alone, not followed by
stretchz load verification, is used. Use of hydraulic bolt
tensioners results in accurate application of initial axial
load to the bolts; however, this initial load is decreased
due to transfer-load losses when the load from the
hydraulic bolt tensioner is transferred to the nut 011 the
tensioner side of the joint. Therefore, if tensioners me
employed to obtain the target residual preload, use the
procedure recommended by personnel who art: experi-
enced and qualified in controlled bolting services. Most
tensioning tools require additional bolt length.
(d) Rt!t5arding direct measurement of residual bolt
elongation, it should be recognized that, if ultrasonic OJ"
micrometer elongation control is used, in itial hol t length
readings must be obtained and documented for each
bolt for which bolt elongation is to be determined: addi-
tionally, compensation must be made for u-mperature
changes in the bolt after the initial length measurement.
For accuracy, the instrument should be calibrated to
properly read the bolts being tightened. lnforrnation
storecl in the instrument or tabled values mClYbe too
generic to produce the desired level of nccuracy. For
bolts constructed with a centerline indicator (gage) rod
as shown in Figs. 1 and 2, neither initial length measure-
rnents nor temperature compensation is required,
thereby allowing direct determination of the true bolt
elongation (and hence bolt stress) for both initial assem-
bly and for troubleshooting purposes during operation.
(e) Proprietary force-sensing devices that can provide
accurate and reliable real-time (increasing and decreas-
ing) bolt tension readings /printouts are available (1'0111
several manufacturers.
10_2 Bolt Elongation (Bolt Stretch) Determination
When bolt elongation (bolt stretch) measurement is
selected CIS the load-control technique to he used, the
required bolt elongation is computed according to the
following equation (assumes the boll' is threaded (ull
length):
~L = (5J
' ~ l-tf')(~\:)
where
Ar root area, mm2 (in.:!). See Appendix 1-[ for bolt
root areas.
= tensile stress area, mm2 (in.2). See Appendix H
for bolt tensile stress areas.
E = modulus of elasticity, MPa (ksi)
Liff = effective stretching length, mrn (in.). The con-
ventional assumption is that the effective
stretching length in a through-bolted joint sys-
tem is the distance between mid-thickness of
the nuts, where the nominal thickness of n
10
, '1, If ,I II (J! 1'1 'I II , I I
II . II·"
ASMEPC(·1-2013
-:2COo,
'" c:_ '".D_
~~
'" '"'" >-0
-1-
" I II , 11 I, I ,
Q)
u
c~~
Q)
a:
(1)
Q)
'"
COt-,, ..c:... en
o :::J
.... 0.~ .c
"Ct-c:
Q;
.D
E
=>z
E
~...o
u,
ASME PCC-1-2013
-£co'"
III c
- III.0_
~:;;III _
:l: ~
-0-J_
Ol
c::.~
~a
IIIu
C~~
III
a:
III
III
shows an example of all approach to selecting
the tools, tightening method, and load-control technique
suitable to the need.
NOTE: Table 'I is provided as an illustration: due consideration
01 specific conditions and factors applicable to the joint under
consideration should be given when selecting the appropriate
tightening method,' load-control technique combination for a given
application.
10.4 Start-Up Retorque
On joints that are problematic, or have been deter-
mined to have insufficient buffer against leakage in
accordance wi thAppendix 0, a start-up retorque may be
performed to decrease the likelihood of leakage during
operation? Start-up retorque is performed when the
temperature of the flange or bolts is between I50aC
(3000P) and 230°C (450°f:) or within 24 h of unit start-
up if the [oint temperature remains below 150°C (300°F).
This temperature range and time window is selected to
allow for the maximum amount of gasket relaxation
prior to retightening while avoiding significant evapora-
tion of lubricating oils from the antiseize product. Loss
of lubricating oils greatly reduces the accuracy of the
torque. The applied torque is sometimes adjusted to
account for changes in antiseize nut factor at the average
start-up retorque temperature. Start-up retorque is typi-
cally not recommended for PTFE-based gaskets. Where
start-up retorque is not practical, live tighteni.ng at a
later stage of operation using tum-of-nut may be used
as an alternative.
The start-up retorque is performed in accordance with
the following procedure:
t ff joint-tightening activities are performed on pressurized
equipment, there is a risk of gasket blowout due to the disruption
of the jnint. Gasket blowout or leakage may occur at a location
around the periphery of the joint other than the one being tight-
ened. This risk should be considered. particularly with respect to
personnel in the vicinity of the joint.
l"'''11 .u t f'in I H II I ~I Itt It" ,...t,\ ... 01 !
(n) The ambient-temperature assembly Target Torque
value should be adjusted to account for any change in
nut factor with temperature.
(IJ) Once the unit is brought online and the metal
temperature is between IS0°C (300°F) and 230°C (450°F)
(commence once the flange reaches the lower tempera-
ture) or within 24 h of unit start-up if the joint tempera-
ture remains below 150°C (300°F), then proceed in a
circular pattern and tighten each bolt. The Lise of
multitool tightening on opposing bolts is an acceptable
practice, but a circular pattern should be used.
(c) Continue tightening in the circular pattern until
the nuts no longer turn.
An engineering and risk analysis of the proposed
start-up retorque operation shall be carried out to estab-
lish that the operation can be performed safely. Start-
up retorque should not be considered the same as live
tightening or hot bolting (see Appendix B). Live tight-
ening or hot bolting are post-assembly activities usually
underta ken due to leakage or maintenance requirements
and are covered further in ASME PCC-2.
11 TIGHTENING SEQUENCE
11.1 Single-Tool Usage
Select from the following:
(a) The Table 4 Legacy pattern and numbering
system.
(IJ) The Table 4,] modified Legacy pattern and nurn-
bering system.
(c) The alternative pattern sequences shown in
Alternatives #1, #2, and #3 of Appendix F; compliance
with the stated limitations for their application is
essential.
The torque increment round-tightening information
for the Table 4 Legacy pattern is detailed in Table 2 (see
Figs. 3 and 4 for an illustration of the Legacy
cross-pattern tightening sequence for a 12-bolt flange
and a 48-bolt flange, respectively, the latter illustrating
the bolt-grouping concept). Counterpart illustrations of
certain alternative pattern sequences are covered in
Appendix F.
NOTE: The cross-pattern bolt-tightening sequence and multi-
rOLLOd tightenJng are necessary to COW1terthe elastic interaction
that occurs when tightening bolts. Sec Appendix I for addinonal
information regarding elastic interaction (01' bolt cross-talk).
11.2 Multiple-Tool Usage
Follow the procedures outlined in Alternatives #,1and
#5 of Appendix F.
11.3 Measurement of Gaps
For the purpose of maintaining parallelism during the
initial tightening passes of assernbl y, take measu rcments
of the gap between flanges around the circumference.
Measurements and adjustments are not needed past this
13
ASME PCC-1-2013
fig. 3 Example legacy and Alternative to legacy Numbering Sequences for 12-Bolt [oint
(a) Legacy (see Table 4) (b) Alternative to Legacy (see Table 4.11
t4
!) I II I l
ASME PCC-1-2013
Fig_ 4 48-Bolt Flange Bolt-Grouping Example
Group
12
Group
2
Group
10
Group
7
Group
6
GrollI' Bolts
1 1-2-3-4
2 5-6-7-8
3 9-10-11-12
4 13-14-15-16
5 17-18-19-20
6 21-22-23-24
7 25-26-27-28
8 29-30-31-32
9 33-34-35-36
10 37-38-39-40
11 41-42-43-44
12 45-46-47-48
Tightening sequence for
12 grOlJPs:
1-7-4-10 ,..1
2·8·5-11 ,..J
3-9-6-12
(The 12-9rOUP sequence
is the same as a tz-bou
sequence: see Fig. 3.)
GENERAL NOTE: This figure is an illustration of how bolts may be grouped for tightening. Bolts may be grouped and tightened treating these
groups as one bolt In the tightening sequence. A suggested number of bolts For a group is the number contained within a 30 deg arc. However.
potential gasket damage or flange misalignment should be considered when bolts arc grouped.
lS
ASMEP((·1-2013
point if the flanges remain parallel. Measure the gap
between flanges at eight or more equally spaced 10cCl-
tions of goOd·QU.llily flange surface around the circum-
ference. Use a measuring device that allows for good
comparison between points. Cap measurements are not
intendedThe
use of substitute gaskets during testing instead of those
designed as the final seal For the joint is not
recorn mended.
Refer to AStviE PCC-2, Article 5.1 for ~eneral good
practices for pressure and tightness testing of pressure
equipment.
14 RECORDS
Consideration should be given to the preparation of
a joint assembly record for each assembled joint, particu-
larly those that are deemed to be in critical service or
deemed to be prone to leakage.
14.1 Documentation of Authorized Agent
As described in the Note at the end of section 2, the
term "user" is understood to include the user or their
author ized agent. Such authorization should be
recorded in either the contract documents or the written
assembly procedures.
14.2 Joint Assembly Records
Joint assembly records may include the following
information:
(a) joint location or identification
(b) joint class and size
(c) specifications and conditions of flanges, fasteners,
washers (including nut- or washer-bearing surfaces),
and gaskets
(d) date of activity (assembly, disassembly, pressure
test. etc.)
(c) names of assemblers/workers
(f) name of inspector or responsible person (see
Appendix G)
(g) disassembly method
(II) adverse disassembly conditions, such as the pres-
ence of nut seizing or thread galling
(i) leak history
(j) bolts, nuts, and washers used
(k) flatness measurements. when made (see
Appendix D)
(I) assembly procedure and tightening method used,
including applicable Target Prestress values as per the
indicated tightening method
(III) unanticipated problems and their solutions
(II) tool data such as type, model, pressure setting,
and calibration identiflcatlon
(0) tool access or safely issues
(I') recommendations for future assembly procedures
and jOint maintenance and repairs
1(1
ASME PCC-1-2013
Fig. 5 Example Short Assembly Record
o
Date of installation: _
Gasket description: _
Final torque used: _
Joint assembled
By: Siqn: _
Joint inspected
By: _
Notes/Problems:
Siqu: _
Return completed record to--7:"IN:-.m-.:-j __
Examples of three different types of joint assembly
records are shown in Figs. 5 through 7. An example of
a joint leakage record is shown in Form P-3.4.
Often, the first step in maintaining joint assembly
records is to uniquely identify each joint. The unique
identifier should ideally be permanently fixed to the
joint using a marking or tag system that enables an
assembler to verify that they have the correct joint prior
to working on it. Such a system enables storage of joint
assembly records against the unique joint identifier and
minimizes the potential hazard associated with disas-
sembly of the vvrong joint.
Joint assembly records have two purposes.
(a) They facilitate joint assembly quality control by
recording the individual responsible for a particular por-
tion of the joint assembly process.
(b) They provide a record of the joint assembly param-
eters that were used and the lessons learned.
The first purpose is achieved by increasing the respon-
sibility of the individual invol ved in assembling the joint
by maintaining a record of their actions and identity.
The second purpose is achieved by documenting the
actual parameters used and observations made during
joint assembly. This information will be useful if the joint
leaks during operation, or for guidance during future
assembly of the joint. It is essential that any deviations,
comments, observations, or changes to the assembly pro-
cedure are feel back into the joint assembly record sys-
tem, such that the assembly procedure may be updated
prior to the next joint maintenance activity.
Users should decide what level of detail to record
based on their own needs and resources. Due to the large
numbers of pressure-boundary bolted joints assembled
during construction and maintenance activities, it may
not be practical to maintain a record of all joint assembly
parameters (i.e., the example record shown in Fig. 7).
Therefore, this sort of record is often completed and
archived only until the next assembly for joints that are
the most critical or most likely to leak. The shortened
record (i.e., the example records shown in Figs. 5 and
6) typically does not include all the joint assembly
parameters or observations and is typically discarded
after the unit start-up. This means that the second pur-
pose is not achieved, but the more important effect of
improving joint assembly quality control is still attained.
There is typically also a register of joints that is main-
tained, in addition to the joint assembly records, which
tracks the progress of each joint, whether there is an
assembly record or not. The register may incorporate
the use of the joint assembly records by requiring visual
confirmation of a completed record prior to the joint
register being updated to show that the joint may be
returned to service.
An additional note of guidance is that the tendency
to provide or request too much information on the joint
assembly record should be avoided. It should not be
considered a substitute for written assembly procedures
or assembler qualification.
15 JOINT DISASSEMBLY
Before any joint is disassembled, it is essential that
assurance be obtained from personnel in responsible
charge of the management of the system that all pres-
sure, including that due to a liquid head, has been
removed from the system and that proper procedures
have been followed to ensure that joints may be safely
opened.
A sufficient number of loosened nuts should be left
in place until all tension has been relieved, to guard
·17
ASMEP((-1-2013
Fig_ 6 Example Medium-Length Assembly Record
BACKFRONT
o
Joint Identification:
Plant name: _
EquipmentjDwg. no.: _
Joint description no.: _
Joint Description:
Diameter: _
Pressure rating: _
Gasket type/size: _
Bolt/nul specification: _
Boll size and lenglh: _
Washer uescriptlon: _
Assembly Parameters:
Assembly method: _
Assembly bolt stress: _
lubricant used: _
Assembly torque: _
Pump pressure: _
Tool Identification:
lisllool calibration identifiers:
o
Joint Assembly Sign-Off:
(1) Disassembled lIange inspected
(2) Gasket inspected pre-installation
(3) Bolt pre-install (free-running)
By: Si9n: _
(4) Joint aligned
By: Sign:
(5) Bolts lubricated
By: Sign:
(6) Joint snug tightened
By: Sign: _
(7) Joint 100% assembled
By: Siqn: _
(8) Joint leak tested (pressure - _
By: 5ion: _
(9) Final OC sign-off
Slgn: D8Ie: _
Notes/Problems:
Return complcled record to--~'N~.'-".~I--'/
18
ASME PCC-1-2013
Fig_ 7 Example long Assembly Record
Joint Identification:
Plant name: Equipment/Dwg. no.: _
Joint description/number: _
Joint Description:
Diameter: Pressure rating:
Gasket type and materials: _
Gasket size (0.0., 1.0., and rhlckness): _
Bolt/nut specification: Bolt size: Bolt length: _
Washer description: _
Assembly Description:
Disassembly procedure required? Yes / No
Assembly method to be used: _
Target assembly bolt stress: _
Torque or tension setting required: _
Assembly rs-torque required? Yes / No
Lubricant to be used: _
Other special instructions: _
Keep failed gasket? Yes / No
Re-torque torque value: _
Tool Identification:
List tool and pump (if applicable) unique calibration identifiers:
Joint Assembly Sign-Off:
(1) Disassembled flange inspected
(2) Gasket inspected pre-install
(3) Bolt pre-install (free-running)
By' Sign: _
Joint Assembly Parameter Records:
Nut/washer bearing surface condition: _
Flange finish and flatness: _
Max. raelial defect Defect clepth: _
Max. run-out: Max. warp: _
(4) Joint alignment
By: Sign:
(5) Bolts lubricated
By: Sign:
(6) Joint snug tightened
By: Sign:
(7) Joint 100% assembled
By: Sign:
(8) Joint leak tested
By: Sign:
(9) Final ac sign-off
Joint alignment:
Max. axial gap: _
Max. alignment loacl: _
Joint in-process alignment:
Max. gap difference @ snug: _
Max. gap difference @ tioht: _
Final pump pressure used: _
Joint leak test:
Test pressure Leak: Yes / No
Action taken if leaked: _
Sion: Date: _
Notes/Problems:
Return compleled record