Document 100L981kbwXVO0GnVM7rKbbZ

BULLETIN 171 1960 Fifth Edition SPIRAL WOUND GASKETS DESIGN CRITERIA I I 390247 i copyRirtHT roan fi fxrrai i it fiasxFT co inc c X G G C r' = .M.,'i i:;c >. c r P.O Bo* 680. Camden, New Jersey 08101 5 Linden Street. Camden, New Jersey 08102 Phone (609) 963-1130 Houston f-;e: P.O. Bo* 760. Deer Park. Texas 77536 Phone (713) 479-3491 Lo: Ange i, Pu 802 Spruce Lake Drive Harbor City, California 90710 Phone (213) 549-7168 Wam European Ofi.oo i r. -;o Flexitallic Gaskets Limited Heckmondwike. Yorkshire. England. Telex 557485 Phone (0924) 405571 other affiliated CC'IL. rc in Australia. Mexico. Scotland. South Africa. Spain. New Zealand. Venezuela West Germany SPIRAL WOUND GASKETS DESIGN CRITERIA Copyright 1980. Flexitallic Gasket Co. Inc. INTRODUCTION This paper has been prepared as the result of many requests received from design engineers, users and others for more detailed information on the ^design and use of FLEXITALLIC spiral-wound gaskets. The concept of spiral-wound gasket construction was originated in 1912 by the FLEXITALLIC GASKET COMPANY. With the introduction of FLEXITALLIC gaskets, a new era in safe, effective sealing of joints was inaugurated. The versatility of this design concept is now attested by the wide range of successful applications, ranging from extremely high vacuums to pressures in excess of present flange standards of 2500 psi and from cryogenic temperatures to beyond 11500F and against virtually every known corrosive media. The FLEXITALLIC design has not only kept pace with modem trends, but has been constantly in advance of such progress that combines materials and construction techniques which result in effective sealing that could not be achieved by any other known type of gasket. Since 1912. the FLEXITALLIC GASKET COMPANY has had a record of steady growth and today is the largest organization in the world that exists solely to produce a spiral-wound gasket. Our entire efforts are directed toward producing for our customers, the highest quality and the most reliable gasket at competitive prices. GO TABLE OF CONTENTS Introduction......................................................................... Available Styles..................................................................... Criteria For Materials Used In Gasket Construction......... | Available Gasket Sizes & Manufacturing Tolerances .... Sizing Spiral Wound Components For Flexitallic Gaskets Flange Surface Finish .......................................................... ASME Boiler & Pressure Vessel Code Calculations........... j Flange Design For Flexitallic Gaskets............................... Ordering Information -- Special Gasket Designs............. Bolting-Up Procedures.......................................................... Appendices: A - Corrosives which can induce stress corrosion cracking in metals ................................. B - Corrosives which induce intergranular corrosion in Austenitic Stainless Steel.................. List of Tables Table No. I. -- Gasket Sizing Limitations ................................. II. -- Gasket Manufacturing Tolerances.................... III. -- Metal Ring Sizing Limitations............................ i IV. -- Gasket Seating Stresses....................................... Page 2 3 5 7 7 9 9 11 11 12 O XT OJ CO O CO 14 15 7 7 8 10 List of Charts and Sketches I Chart No. 1 -- Flange Width vs. Diameter........................................................................................................................................8 J Sketch No. 1 -- Bohing Diagrams................................................................................................................................................... 13 I Chart No. 2 -- Bolting Data for Standard Flanges..................................................... 15 i. 390248 390249 Caskets are essentially a packing designed for inclusion between rigid parts of a fluid container in an essentially stationary relationship. A FLEX1TALLIC gasket consists of laminated, preformed metal strips and filler materials selected to meet the conditions of service required. Its construction provides inherent resilience enabling it to follow flange movement within reasonable limits. Unfortu nately, gaskets are all too often simply accepted per se, that is, "just another gasket." The irony of this is that one of the most costly and serious industrial problems today is leaky joints resulting in explosions, fires, loss of production and soaring maintenance costs. Much of this is due to insufficient attention to the proper application and design of closures and the gaskets that are used to effect the seal. The FLEXITALLIC gasket is not "just another gasket." It is a specifically engineered product in the FLEXITALLIC program of continuous research and development in gasket design and production control to give you assurance of quality and safety. It is our objective in the preparation of this bulletin to help prevent, through greater knowledge of the FLEXITALLIC gasket, the serious and costly waste of time, money and resources resulting from joint leakage. We trust the information contained herein will prove worthwhile and will benefit the equipment manufacturer, design engineer, and the user in sealing closures, whether high or low pressure, high or low temperature, and regardless of the nature of the corrosive media to be sealed. HOVi FLEXITAL LIC GASKETS ARE ,'.iAMU FC<C 7U RED A FLEXITALLIC gasket is manufactured by spirally winding a preformed metal strip and a filler on the outer periphery of metal winding mandrels. The winding mandrel outside diameter forms the inner diameter of the gasket and the laminations are continually wound until the required outer diameter is attained. Normal practice is to reinforce the inner and outer diameters with several plies of metal with no soft fillers being introduced. Our method of manufacture includes custom designed devices which provide control of gasket density that permit compression to the operating thickness under a specified load. This engineered product is thus "tailor made" to be compatible with the flanged closure in which it is to be used. For example, a closure designed for vacuum service may require a gasket of exactly the same dimensions as a closure designed for 1500 psi service. The closure designed for the vacuum service would have relatively light bolting indicating the necessity for a soft gasket, while the 1500 psi application would have heavy bolting indicating a relatively dense gasket. It is usually within our capability to satisfy both requirements. Refer to paragraph on "Range Design for Rexitallic Gaskets." AVAILABLE STYLES OF FLEXITALLIC GASKETS Cmi ^ ' U *+ I 3 3 0 9 1. Style R-------This designates a round spiral-wound gasket with no accessory devices added. The notations, Rl, R3, and R4 in our catalog, apply to our standard gaskets only, so indicated for use on standard flanges. If a Style R gasket is to be used on a special flange design (other than ANSI or BS flange specification), the gasket is usually termed a Special Style R. 3. Style CG------ A Style CG gasket is a round, spiralwound gasket with a solid metal outer ring forming a complete assembly. The outer ring serves as a compression stop, anti-blowout device, and to properly center the gasket on the flange. 2. Style RIR------ This is a round spiral-wound gasket fitted with an inner metal ring used to provide inner confinement to the gasket, to act as a compression stop if of the proper thickness, and to be used to fill the annular space between the flange bore and the gasket I.D. to minimize turbulence of process fluids and erosion of flange faces. 4. Style CGI Gasket------ This designates a CG gasket as above with the addition of an inner metal ring. The inner ring thickness is normally the same as the outer ring and serves to prevent material build-up between the flange bore and the gasket I.D., as a protection against excessive heat, to reduce process fluid tu bulence and to minimize erosion of flange facings. Style gqi gaskets are frequently used on vacuum service and for PTFE gaskets. This style eliminates costly machining in one of the flange faces if a totally contained gasket is requited. A Style CGI gasket wiiJ effectively provide a totally contained gasket without the additional costly machining. 5. Style CG-RJ------- This style designates a Special CG gasket sized to be used on standard ring joint flanges as noted in our catalog. The outer ring is dimensioned to cover the ring joint grooves and to prevent the spiral-wound portion from entering the groove. The spiral-wound portion of the gasket is sized to fit between the flange bore and the ring joint groove. This type of gasket should be used only as a maintenance repair item, if FLEXTTALL1C gaskets are to be used in new construction, it is advisable to use standard raised face flanges and our Style CG gasket. 390250 Please note Style T ~^'..ts rely on internal pressure in the boiler to properly scat the gasket. This means, when a hydrostatic test is performed on the gasket, the pressure exerted against the plate will farther compress the gasket -- and it is necessary to tighten each nut to compensate for the additional compression of the gasket under load. RCL'N^ cercund OR flat.SIDED OR straight-side; square CR RECTANGULAR 6. Style D-------This consists of a spiral-wound gasket with loops (usually 2) added to the O.D. of the gasket and dimensioned to fit over two diametrically opposite flange bolts for centering purposes. Style D gaskets are not generally recommended for use in applications where pressures are in excess of 600 psi. It is not as widely used or as popular as the Style CG gasket, with its outer metal ring functioning as a centering, anti-blowout device as well as a compression stop. The Style D gasket does lend itself to ease of assembly in areas of congested piping plus the fact that the standard Style D's are less expensive than the CG for the equivalent size ana pressure rating. When Style D gaskets are required and are not standard catalog items, special winding mandrels must be purchased. It should be noted, the spiral-wound portion of the Style D gasket is identical to the spiral-wound portion of a Style CG gasket in the same size and pressure series. 8. Sle M & MC-------These styles are designed for boiler manhole cover assemblies. They are usually of round, obround or oval shape, depending, of course, upon the manhole plate configuration. Style MC gaskets have a preformed spiral-wound centering ring snapped into the inner groove of the gasket proper. This centering guide permits the gasket to assume its correct position and to compensate for inequalities in plate contours and fillets in cold-pressed plates as well as to prevent shouldering and pinching caused by radial misplacement. 9. Style HE------ Style HE gaskets are for heat exchangers where pass ribs are required. The outer portion is of standard spiral-wound construction, whereas the rib portion is normally of single or double-jacketed style, securely fastened to the ID. of the spiral-wound portion. GO I CD jr- CO CO O 7. Style T-------This designates gaskets for boiler handhole and tube cap assemblies. They are available in round, oval, obround, square, pear and diamond shapes. Refer to our general catalog for standard Style T gaskets. 4 10. Style HE-CG ------- This style is identical to the Style HE above, except that it is fitted with an outer ring on the O.D. Note ------- Style HE eod Style HE-CG gaskets have a primary seal of spiral-wound construction with its inherent resiliency and excellent sealing quality. It is necessary that dimensional drawings locating the pass ribs and the configurations be submitted for ell inquiries and orders for these style gaskets. 390251 11. Style HX*------ Sty ie HX gaskets are suitable for standard heat exchanger flanges designed in accordance with BS 3274 and TEMA standards. The primary seal is a spiral wound gasket construction which is fitted with a stainless steel outer wound guide so as to correctly locate the gasket in the flange recess. An inner compression stop ring is fitted and for the tubeplate to channel connection, a compressed asbestos fibre insert with pass partition bars is incorporated. Where working conditions demand it. the compressed asbestos fibre insert can be dispensed with and the pass partition bars can be supplied in metal asbestos or solid metal as part of the inner compression stop ring. 'Note------- Submit application to Engineering Department 12. Style 625 ------ Similiar to Style R gaskets, except The selection of materials of construction for FLEXiTALLIC gaskets requires consideration of the following aspects: 1. The corrosive nature and concentration of the' fluid to be confined. 2. The operating temperature. 3. The expected life of the installation. 4. The relative cost of alternative materials. Specific recommendations for materials of construction are beyond the scope of this paper. The resistance to corrosive attack by the various materials used in FLEXITALLIC gaskets fluctuates widely, depending upon the concentration of the corrosive agent, presence of other contaminates and the operating variables of temperature and pressure. Lacking specific experience with the corrosive nature of any particular agent and those materials that would have sufficient corrosion resistance to the media, designers are recommended to contact the manufacturers of alloyed materials, who have available extensive information on the chemical resistivity of their products to various corrosive media. Another excellent source of corrosion resistance is contained in "Corrosion Data Survey" pub lished by the Association of Corrosion Engineers, Houston, Texas. It is frequently necessary to conduct laboratory corrosive tests and/or pilot plant operations in order to obtain factual and reliable information. When considering the choice of materials for FLEXITALLIC gaskets, designers should be guided by the following general comments: 1. Stress Conosion -- FLEX1TALL1C gaskets, when installed, are highly stressed, particularly in the area of the engineered wire formation, and adjacent to the flange seating surfaces. The 18-8 stainless steels are particularly subject to stress conosion or stress corrosion cracking when exposed to certain media. Corrosive materials that induce stress corrosion cracking in metals are included in Appendix A. In such cases, alternative materials must be selected that are less susceptible to stress corrosion cracking. original thickness is .0625". Limited to small diameters and narrow flange widths. Most frequently used on clamp-tvpe closures where an extremely thin gasket is required. 13. Miscellaneous-------- On rare occasions, applications for FLEX1TALLIC gaskets arise where it is necessary' to utilize a spiral-wound inner and/or outer ring. The spiral-wound inner or outer rings are used primarily as centering devices and are chosen in lieu of a solid metal nn g. because of lower cost or because of limited space when the use of a solid metal ring would be prohibited because of the difficulty in fabrication. Refer to our General Catalog for FLEXITALLIC gaskets available for standard flanges and common boiler handhole and manhole fittings. STOLI 33 I I ED !M GASKET CCKSTRUCT'CX 2. Intergranular Corrosion -- When austenitic stainless steels are subjected to temperatures in the range of 800 to 1500F, carbides are precipitated along the grain boundaries. When exposed to certain chemicals, inter granular corrosion will occur. A list of corrosives which induce intergranular corrosion are included in Appendix B When handling these media, special attention to material selection is necessary. 3. Expected life of the Installation -- The trend in industry today is to lengthen the time between overhauls and consequently, the best possible material, regardless of initial cost, is frequently the most economical. Gaskets are relatively low cost items when compared to labor costs to install, downtime on equipment and loss of productivity, should premature failure occur. Hence, for "permanent installations, the cost of special gasketing materials should be equated against increased productivity and reliability. The FLEXITALLIC GASKET COMPANY maintains a substantial inventory of a wide variety of metals and filler materials to meet specific operating conditions and requirements. METAL WINDINGS The following materials are normally inventoried to insure prompt delivery: Type 304 Stainless Steel -- This 18-8 Chromium-Nickel Steel is the most common metal used in the fabrication of FLEXITALLIC gaskets. It has excellent corrosion resistance to a wide variety of chemicals. It is, however, subject to stress corrosion cracking when exposed to certain media, and to intergranular corrosion at temperatures between 800F and 1500F in the presence of certain media. Under these conditions, alternative materials should be selected. Due to the precipitation of carbides along grain boundaries, its use is normally limited to a maximum continuous temperature of 800F if any danger of the materials that would cause intergranular corrosion are expected to be present. 390252 Tv pe 34" Stainless Sleei -- The audition m aorammum to this 1 .S-i0 Chromium-Nickel Steel ser.e to keep carbides in solution, and hence, inhibits carbide precpnation along the grain boundaries. Type 347 Stainless Steel fr-. corrosion resistant qualities comparable to Type 304 Stainless Steel. It is not as subject to intergranular corrosion as is Type 304 Stainless Steel, and can be used at continuous temperatures up to the 1400--1 500F range. Type 347 is subject to stress corrosion cracking, however, as is Type 304. Type 3 I 6L Stainless Steel -- The 277 molybdenum added to this IS-12 Chromium-Nickel alloy increases its creep strength at elevated temperatures. Carbon content is held at a maximum of .03% which inhibits the tendency toward carbide precipitation. Type 316L is subject to stress corrosion cracking and also to intergranular corrosion, but to a lesser degree than Type 304 Standee Steel. Its continuous maximum temperature exposure would be in the range of 1400--1500F. Type 321 Stainless Steel -- This austenitic Chrome-Nickel Steel is stabilized by the addition of Titanium, thereby eliminating carbide precipitation and consequently inter granular corrosion. The higher chromium content of this grade gives improved oxidation resistance and so it can be used at temperatures up to 1400/1500F. Type 304L Stainless Steel -- This 18-8 stainless steel alloy has the same excellent corrosion resistance as does Type 304. but its carbon content is maintained at a maximum of .037;. which tends to reduce the precipitation of carbides along grain boundaries, and as a consequence, would be less subject to intergranular corrosion than is the Type 304 stainless steel. It is, however, subject to stress corrosion cracking. Plated Low Carbon Steel -- In FLEX1TALL1C gasket construction, the use of this metal is normally limited to low pressure steam applications at maximum temperatures in the range of 500F. Monel Metal -- This Nickel base alloy contains 677; Nickel and 30% Copper. It is widely used as a gasketing material due to its excellent resistance to most acids and alkalis, except the strong oxidizing acids. In combination with PTFE. it is widely used in FLEX1TALLIC gaskets for hydrofluoric acid service. Maximum upper temperature limit for Monel metal is in the range of I 500F. Monel metal is subject to stress corrosion cracking when exposed to fluorosilic acid, mercuric-chloride and mercury, and should not be used with these media-,-- Inconel 600 -- This metal is a Nickel base alloy containing 7777 Nickel, 15% chromium and 7% iron. It has excellent high temperature strength and can be used at temperatures up to the 2000F range. Inconel 600 has little tendency toward stress corrosion cracking and is frequently used as a gasketing material to overcome this problem. Oil'! K ML 1 \Lx A\ All Mil I MATERIAL MAX/TEMPERATURE* 430 S.S................................................................ 1400/I500F Carpenter 20 ...................................................... 1400/1500 F Phosphor Bronze ..................................................... 500"F Nickel ........................................................................ 1400" F Titanium...................................................................... 2000'F Hastelloy C-276 & B................................................. 2000F Inconel X..................................................................... 2000F Copper............................................................................ 500F 310 S.S........................................................................ I 900F On special order, gaskets can be fabricated from gold, zirconium, platinum and tantalum. * Maximum temperature ratings are based upon hot air at constant temperatures. The presence of contaminating fluids and cyclic conditions mav drastically affect the maximum temperature range. FILLER MATERIALS 1. Canadian Asbestos Paper (Chrysottle) -- Canadian Asbestos Paper is the most common filler material used m the fabrication of FLEXITALLIC gaskets. Canadian Asbestos is a hydrated magnesium-silicate. The form, as we use it, is composed of approximately 90% Canadian Chrysotile Asbestos. 7% vegetable rubber iatex binder and 3% water-proofing binder. This material has poor acid resistance and strong mineral acids dissolve out ail magnesia, leaving a residue of nearly pure insoluble silica It does, however, show excellent resistance against alkaline solutions, such as sodium-hydroxide or caustic sod3 and can be used against solvents, aqueous and salt solutions, and gases (except oxygen). Canadian Asbestos has a very high melting point fusing at approximately 2770F. However, it loses 11% by weight of water at 1100F and about 13.5% at 1400F. From this point to the fusion temperature, it has turned to a powder with very little tensile strength left. In spite of this, it can continue to produce a satisfactory seal since it is completely confined between the metal windings of the gasket and the seating surfaces of the flange. Our standard Canadian asbestos paper contains .1% blue vegetable Jve for identification purposes. This material is available without the dye added if the possibility of color contamination is a problem. Note: All asbestos paper used by FLEXITALLIC GASKET COMPANY is tested for teachable chlorides and meets the 200 parts per million requirements for total soluble chlorides. 2.Compressed Asbestos Fiber Type Special -- This is a grade of compressed asbestos fiber specially developed for use in spiral wound gaskets. The homogeneous structure of the materia] allows it to more readily conform to the spiral wound steel profile than conventional compressed asbestos fiber materials. The material contains an asbestos content of 70% and a binder content of 12%, this being a blend of NR and SBR. The material shows good performance in steam and hydrocarbon service at high temperatures. 3. Polytetrafluoroethylene (PTFE) -- PTFE c used as a filler material in FLEXITALLIC gaskets where extreme chemical inertness is required for temperatures ranging from cryogenic to 500F. PTFE is unaffected by any known chemicals except molten alkali metals and fluorine precursors. Because of its low permeability, PTFE is also frequently used as a filler material on FLEXITALLIC gaskets in vacuum applications. Gaskets wound with PTFE dtoukl be fully confined either by fitting in a groove or providing both an external and internal ring. 4. Ceramic Fiber Paper-- Consists of aluminum silicate fiber with an organic binder. This material has excellent high temperature stability to 2300F. It resists attack from most corrosive agents (except hydrofluoric and phosphoric acids) as well as concentrated alkalies. 5. Flexicarb -- This material is a pure pyrolytic graphite with no binder which exhibits excellent resistance to a wide variety of chemicals. Flexicarb can be used in the temper ature range from -350F to 900F in an oxidizing atmosphere and up to 6000F in a reducing or neutral 390253 atmosphere*. Its unique combination of low permeability inherent lubricity, and compressibility make Flexicar suitable for critical gas services. *Note: We suggest applications for oxidizing atmospheres supmrfred ro Engineering Department. 6. Other Materials -- FLEXITALLIC gaskets are als available with various compressed asbestos sheet packing utilizing Buna S, Neoprene, or Buna N as a binder fc special applications. Gasket Thickness 0.0625" 0.0625 0.100 0.125 0.125* 0.175 0.175* 0.175* 0.175* 0.250 0.285 Max. I.D. Up to 6" 6 to 9 10 Up to 20 20 to 40 Up to 40 40 to 60 60 to 70 70 to 75 90 ISO TABLE 1 Max. Flange Width 3lnr 1/4 1/2 See Note 4 3/4 See Note 4 1 7/8 3/4 1 1 Recommended Compressed Thkns. 0.050" AJ.055" 0.050/0.055 0.075/0.080 0.090/0.100 0.090/0.100 0.125/0.135 0.125/0.135 0.125/0.135 0.125/0.135 a 180/0.200 0.200/0.220 Notes: 1) All dimensions in inches 2) Preferred size range in relation to thickness shown in bold type 3)*PTFE filled FLEXITALLIC gaskets in this size range are unstable and are subject to "springing apart" in shipping and handling. Specify next gasket thickness up. 4) See chart No. f. page 8 for recommended gasket widths. 51 ** The recommended compressed thickness is what experience has indicated to be the optimum range in order to achieve maximum resiliency of the gasket. An additional spread of .010 in either direction may be tol erated on all gasket thicknesses with the exception of the 0625 and the .100" thick gasket. This is on the assumption that the flange surface finishes are relatively smooth. Refer to "Flange Surface Finish" on page 9. When attempting to contain hard to hold fluids, or pressures above 1000 psi, it is suggested that compression be maintained St the lower range of the recommended compressed thickness. SIZING SPIRAL WOUND COMPONENTS FOR FLEXITALLIC GASKETS Regardless of the type of flange facing in use, FLEXI TALLIC gaskets must be sized to insure the spiral-wound element is seated against a flat surface. This is of utmost importance. If the spiral-wound element protrudes into the flange bore jjr extends beyond a raised face, mechanical damage will occur to the gasket during initial compression, and ultimate failure will result. In addition, should the gasket protrude into the flange bore, the windings can possibly enter the process stream with severe damage to other equipment resulting. With recessed flange facing?, limiting dimensions of the gasket are established by dimen sions of the groove. On flat or raised face flanges, considerable k. vay is available. The following rules will be goerally a; "licable for limiting dimensions of spiralwound components. (See Chart I for nominal flange widths.) FLEXITALLIC gaskets are available in sizes from i/2 I.D. to approximately 150" I.D. depending upon gaskt thickness. Table I indicates size ranges available in vanoi thicknesses, maximum flange widths and the recommende compressed thickness. FLEXITALLIC gaskets are subject to standard mam factunng tolerances listed in Table II. If tighter tolerano are required, consult our Engineering Department. TABLE II Gasket Diameter Up to 10" 10" to 24" 24"to 60" 60" & Above I.D. + 1/64 1/32 + 3/64 + 1/16 O.D + 1/32 + 1/16 + 1/16 + 1/16 Tolerance on gasket thickness is plus 0.010", minus 0.005' (measured across metal winding) on all thicknesses. ST04133/3 1. Gasket confined on both ID. &. OD. -- This is the type facing encountered in tongue and groove joints, and groovt to flat joints. Standard practice is to allow a 1/16" normna diametrical clearance between the IT), of the groove anc the I.D. of the gasket and 1/16" nominal diametrical clear ance between the OD. of the gasket and the O.D. of th< groove.* 2. Gasket confined on the OJD. only -- This is the type o facing encountered with male and female facings an< female to flat facings. Standard practice is to allow a 1/16' nominal diametrical clearance between the OJD, of th' gasket and the OJD. of the groove* If possible, allow minimum 1/4" diametrical clearance between the ID. o the seating surface and the ID. of the gasket NOTE: 1/16" nominal O.D. dearanca for gaskets up to 60" O.D. from 60" O.D. to 80" O.D., allow 5/64"; above 80" O.D., allov 3/32" nominal O.D. clearance. 390254 CHART NO ' Graph of Gasket Width/Inside Diameter far RaxitsJlic Spiral Wound Gaskets (Refer to Table 1 for Maximum Flange Width for Various Thicknesses) 6ASKET WIDTH - INCHES' _i-------------------------- 1------------- 1------------- 1 6.3 I2J 18.8 23 CASKET WIDTH - MILLIMETRES 3. Gasket unconfmed on both the IX). & OX). -- Allow a minimum 1/4" diametrical clearance between the gasket IX). and the I.D. of the seating surface. The OX), should be kept as close as possible to the bolt circle to minimize flange bending moments. If the gasket is used with raised face flanges, allow a minimum 1/4" diametrical clearance between the gasket OXi. and the raised face OX), and determine the IX). on the basis of the desired flange width. Important -- Please note the above rules establish general limits for sizing FLEXITALLIC gaskets. It is frequently necessary to adjust dimensions in order to achieve a proper balance between gasket area and bolt area to maintain a reasonable compressive force on the gasket and a minimum gasket factor "m" of three. Please refer to section covering ASME Boiler and Pressure Vessel Code. 4. Metal Gauge Rings -- When FLEXITALLIC gaskets are required to be equipped with outer metal rin^ or with inner metal rings, limitations on the minimum flange widths of the solid metal ring are necessary due to the availability of machining facilities and rigidity of completed assemblies. Table III indicates the minimum flange width for solid metal rings based on the ring IX). TABLE HI Diameter of Ring UP to 10" I.D. 10" to 24" I.D. 24" to 50" I.D. 50" to 70" I.D. 70" and Larger Minimum Flange Width* 3/8" 7/16' 1/2" 5/8" 3/4" Note: Where space is limited and narrower flange widths are necessary, it may be possible to supply inner and outer spacer rings of solid metal spiral-wound construction. Consult our Engineering Department for advice. Standard practice is to size outer rings with the outside diameter equal to the diameter of the bolt circle less the diameter of one bolt for rings up to 60" OX). Above 60" OX)., rings are sized to the diameter of the bolt circle less the diameter of one bolt hole. Inner rings are normally sized with an inside diameter equal to the flange bore plus 1/8". 5. Non-Circular Gaskets -- FLEXITALXJC gaskets can be fabricated in non-circular shapes within limitations. As a general rule, if the ratio of the long IX). to the short IX). exceeds 3 to 1 and should any of these sides approach a straight line, it may not be possible to manufacture a FLEXITALLIC gasket that would be suitable. Our product requires a definite radius or curvature to give it inherent strength and stability and to prevent it from springing apart. Any application requiring a non-circular gasket should be submitted to our Engineering Department for review to determine the feasibility of producing a satis factory gasket as early as possible in the design stage. The comments above relating to availability of sizes and recommended clearances for proper sizingof FLEXITALLIC gaskets are general in nature. Many applications will arise where the recommended clearances are impractical due to space limitation on the flange. Frequently, clearances between gasket sealing member and grooves must be reduced in order to effectively maintain a seal under operating conditions, particularly when the higher pressures are encountered. Under such circumstances, FLEXITALLIC GASKET COMPANY engineers should be consulted prior to finalizing designs. ST04I 3314 FLANGE SURFACE FINISH FLEXITALLIC gaskets rely on the combined reaction of the metal and filler material to effect a seal. When the gasket is compressed, the filler materia] flows into minute imper fections and the metal serves to completely trap the filler material and provide the necessary strength and resilience to the gasket assembly. Obviously, the deeper the serra tions, or the rougher the flange surface finish, the higher the force required to flow the gasket into the imperfections. Although FLEXITALLIC gaskets may seal against virtually any commercial flange surface finish, abnormally high bolt loads may be required to obtain a seal against rough flange finishes, while exceptionally smooth surfaces may destroy the inherent resiliency of the gasket. Surface finish is of major importance when attempting to seal a joint with a FLEXITALLIC spiral-wound gasket! For virtually all ser vice conditions, it is suggested that surface finish be spec ified on manufacturing drawings as a range of 125 to 200 AARH, with a circular lay (either concentric or phono graphic). Surface finishes smoother than this can present a sealing problem. Important -- Under no circumstances should flange seal ing surfaces be- machined in a manner that tool marks would extend radially across the seating surface. Such tool marks are practically impossible to seal regardless of the type of gasketing material used. STU I 33 I 54 ASME BOILER AND PRESSURE VESSEL CODE CALCULATIONS Section Mil, of the ASME Boiler & Pressure Vessel Code, establishes criteria for flange design and suggests values of "m" (gasket factor) and "y" (minimum gasket seating stress) as applied to spiral-wound gaskets. For the most part, the defined values have proven successful in actual applications. However, much confusion exists regarding these values, primarily due to a misunderstanding of the definitions of the terms and their significance in practical applications. Mandatory Appendix II, in Section Mil of the Boiler Code, requires in the design of a bolted flange connection, complete calculations shall be made for two separate and independent sets of conditions. 1. Operating Conditions Condition one (1) requires a minimum load be determined in accordance with the following equation: (1) wml = --2b 3.14GmP This equation states the minimum required bolt load for operating conditions is the sum of the hydrostatic end force plus a residual gasket load on the contact area of the gasket times a factor times internal pressure. Stated another way, this - equation requires the minimum bolt load be such that it will maintain a residual unit compressive load on the gasket area that is greater than internal pressure when the total load is reduced by the hydrostatic end force. It should be noted that Table UA-49.1 suggests a gasket factor "m" for a spiral-wound gasket of 2.5 for carbon steel and 3.0 for stainless or monel. It is important to note the gasket factor "m" is suggested and is not mandatory. (Note: See paragraph on gasket factor "m" on page 10 for a more detailed discussion.) 2. Gasket Seating Condition two (2) requires a minimum bolt load be determined to seat the gasket regardless of internal pressure and utilizes a formula: (2) Wm2 = 3.14bGy* The "b" in this formula is defined as the effective gasket width and "y" is defined as the minimum seating stress in psi that depends upon the type of gasket material. Table UA-49.1, Section Mil of the Boiler Code suggests a minimum "y" value for a spiral wound gasket of 10,000 psi (Winter 1976 Addenda). These design values are suggested and not mandatory. The term "b" is defined as: b = bo when b0 = 1/4' b= when b0 > 1/4" In the case of a spiral-wound gasket, b0 = --N in all cases where N is the radial flange width of the spiral-wound portion of the gasket. NOTE: When Wm2 is greater than Wml FLEXITALLIC suggests recalculating Wm2 using b*N and G*mean diameter. After Wm] and Wm2 are determined, the minimum required bolt area, Am is determined as follows: Wml Am] = ~Si, whet6 Sb is the allowable bolt stress at b Wm2 . _ operating temperature, and Am2 = where Sa is the allowable bolt stress at atmospheric temperature. Then Am is equal to the greater of Am] or Am2- Bolts are then selected so the actual bolt area, Ab, is equal to or greater than Am. At this point, it is important to realize the gasket must be capable of carrying the entire compressive force applied by he bolts when prestressed unless provisions are made to utilize a compression stop in the flange design or by ;he use of a compression gauge ring. For this reason, EXITALLIC'S standard practice is to assume W is SSS06E 390256 equal to Ab Sa.* We are then able to determine the actual unit stress on the gasket bearing surface. This unit stress. Sg, is calculated as follows: Ab Sa (3) Sg = ------=----------------------- (psi) Using the unit .785(010-. 125)J - (dj)3 stress we can assign construction details which will lead to the fabrication of a gasket having sufficient density to carry the entire bolt load. This is the gasket density used by FLEX1TALL1C in assigning construction details for fabrication in our shops. Following this procedure, once Ab has been determined, we are no longer concerned with which is greater, Wm | or Wmi. We are concerned with actual values. If the values of Sg are within the unit stress range indicated in Table IV, a suitable gasket can be provided. If the values determined are greater than those listed, either a wider gasket is required or a compression stop must be utilized. GASKET SEATlMG STRESS---- "y" Flexitallic's past position regarding the unrealistic low value of "y" as defined in Table UA-49.1 has been recognized by the recent change (Winter 1976 Addenda) to "y" = 10,000 pa minimum (formerly "y" = 2500 psi for carbon steel and "y" = 4500 psi for stainless steel). Our experience indicates this new minimum value is, in general, satisfactory for designs utilizing FLEXITALLIC Gaskets. If gasket proportions as indicated on Chart 1 are followed, Table IV can be used as a guide to "y" (minimum seating stress) and Sg (actual stress). The actual seating stress is a function of flange surface finish, gasket material, density, thickness, fluid to be sealed and allowable leak rate. Rough or irregular flange finish, difficult to contain fluids and specified low allowable leak rates all indicate the need for different "y" values. Additional work to deter mine the effect of these variables is indicated and is presently being sponsored by a sub-group of the Pressure Vessel Research Committee, Welding Research Council. Work is also being done to this end by ASTM Committee F-3 and Flexitallic Gasket Company. Sg and "y" are normally con sidered to be the unit load required ' compress the gasket to its optimum operating thickness. Canadian asberros filled PTFE filled Flexicarb filled TABLE IV GASKET SEATING STRESSES 'V' Sg (minimum seating stress) PSI (actual unit stress at gasket bearing surface) psi 10,000 10,000 10,000 10,000 to 25.000 10,000 to 13000 10,000 to 20000 GASKET FACTOR "m" Appendix II, Section VIII, of the Boiler Code under paragraph VA49 makes the statement "the Tn' factor is a function of the gaskel material and construction." We do not agree entirely with this interpretation of "m". Actually, the gasket does not create any forces and can only react to external forces. We believe a more realistic interpretation of "m" would be "the residual compressive force exerted against the gasket contact area must be greater than internal pressure when the compressive force has been relieved by the hydrostatic end force." It is the ratio of residual gasket contact pressure to internal pressure and must be greater than unity otherwise leakage would occur. It follows then, the use of a higher value for "m" would result in a closure design with a greater factor of safety. Experience has indicated a value of 3 for "m" is satisfactory for flanged designs utilizing FLEXITALLIC gaskets regardless of the materials of construction. In order to maintain a satisfactory ratio of gasket contact pressure to internal pressure, two points must be considered. First, the flanges must be sufficiently rigid to prevent unloading the gasket due to flange rotation when internal pressure is introduced. Secondly, the bolts must be adequately prestressed. The Boiler Code recognizes the importance of pre stressing bolts sufficiently to withstand hydrostatic test pressure. Appendix S, in the Code, discusses this problem in detail. NOTATIONS Ab Actual total cross-sectional root arfca of bolts or section of least diameter under stress; square inches. Am Total required cross-sectional area of bolts, taken as greater of Ami, or Am2i *quare inches. Ami " Total required cross-sectional area of bolts required for operating conditions; square inches. Am2 Toul required cross-sectional area of bolts required for gasket seating; square inches, b Effective seating width; inches. 2b Joint-contact-sortace pressure width; inches, bo * Basic gasket seating width; inches. G " Diameter of location of gasket load reaction; inches, m Gasket factor. N - Radial flange width of spiral-wound component; inches. P Design pressure; psi. Sa " Allowable bolt stress at atmospheric temperature; psi. Sb " Allowable bolt stress at design temperature; psi. W " Flange design bolt load; pounds. Wrnl Minimum required bolt load lor operating conditions; pounds. Wm2 " Minimum required bolt load for gasket seating; pounds, y " Minimum gasket seating stress; psi. Sg - Actual unit stress at gasket bearing surface, psi. do Outside diameter of gasket, inches, d, Inside diameter of gasket, inches. (`Note; If a prestress greater than Sa is to be used (as. is normal practice in order to successfully pass a hydrostatic test) the actual prestress value will be used in lieu of Sa in equation (3).  CO ^ CD ZSS06C FLANGE DESIGN FOR FLEXITALLIC GASKETS 1. Determine the required boh load for operating conditions necessary to provide a compression stop either by utilizing Wmi, (Equation (1). (Approximate gasket sze by referring a ring on the inside or the outside of the gasket or by to Chart I and Table I, and use an "m" value equal to designing into the flange, a compression stop that would three.) 2. Determine the required bolt load to effect a seal (W^^ by solving equation (2). Use a minimum seating stress "y" per Table IV. 3. Determine the minimum bolt area by dividing Wmi by the allowable bolt stress at operating temperature and by dividing Wm2 by the allowable bolt stress at atmospheric temperature. The greater of these two values becomes Am, the minimum bolt area. Select the number and size of bolts that will give an actual total cross sectional area equal to or greater than Am. bring the flanges metal to metal. 5. If Wm2 is substantially greater than Wmj resulting in a greater bolt load than required for operating conditions, it is possible to reduce Wm2 by reducing the flange width of the gasket. If This is the case, we suggest you contact FLEXITALLIC engineers for recommendations as to minimum flange widths for the diameter and pressure/ temperature conditions. 6. Proceed strictly to the flange design procedures in Appendix Ii of the Boiler Code. 7. After all flange dimensions have been determined, 4. Substitute the larger of Wmj and Wm2 into the numer determine flange "rotation at the gasket interface at test ator of equation (3) and solve for "Sg". If "Sg" falls within the ranges shown on Table IV, a FLEXITALLIC Gasket can be designed to carry the load. If the resulting Sg conditions. If the flange rotation is excessive, extra ordinary precautions must be taken to insure a satisfactory hydrostatic test. (Refer to section covering "Bolting Up is greater than the maximum indicated in Table IV, it is Procedures.") ORDERING FLEXITALLIC GASKETS FOR SPECIAL FLANGE DESIGNS I I In order for the FLEXITALLIC GASKET COMPANY to design a gasket suitable for the application, it is imperative that complete details be submitted for review. The information we require is the following: 1. Type of flange facing 2. Dimensions of the gasket seating surfaces 3. Number, size and material of bolts 4. Bolt circle diameter 5. Operating pressure & temperature (Process material if known) 6. Hydrostatic Test pressure 7. Initial bolt pre-stress 8. Customer preference on gasket materials FLEXITALLIC supplies engineering data sheets at no cost on which this information may be submitted. As a gasket manufacturer, it is impossible for us to review every flange design to make certain that flange rotation and flange stresses are within allowable limits defined in the Code. We proceed on the assumption the design engineer has followed the design criteria established by the ASME Boiler Code and that the flanges are sufficiently rigid under the most severe condition to preclude the possibility the gasket could become unloaded either during operating conditions or hydrostatic test conditions. We are aware that most flange designers do not take into consideration, flange rotation at test conditions. This is a very important aspect that is not normally considered, and we urge every flange designer to check out flange rotation at test conditions prior to finalizing his design. We also, of a practical necessity, must assume the bolt material being used is adequate for all conditions including operating pressure at operating temperature and hydrostatic test pressure at ambient temperature. The use of the optimum materia1 t3&cUaffic. BASKET ENGINEERING DATA for bolts ts a very complex subject and we suggest ASME paper, number 52-PET-7 entitled "Modern Steel Bolting for Piping & Pressure Vessels", authored by C. M \ ogrin. Frank S. G. Williams and John S. Worth, be con.-,ued for guidance in the proper selection of bolting r a! for piping and pressure vessel applications 390258 BOLTING-UP PROCE: FLEXITALLIC GASKET COMPANY supplies thousands of different gaskets for special flange designs that must successfully pass a hydrostatic test and maintain a satis factory seal under operating conditions. Our experience has indicated that virtually every time a leaky joint is encountered, the actual cause of failure relates to some thing other than the gasket design. These causes are itemized below: 1. On low pressure applications, flange designers have followed the Code suggestions for a minimum seating stress (y value) that we know from experience are impractical and hence, neither the bolting nor the rigidity of the flanges, are adequate to initially seat the gasket to obtain a sea1. 2. Flange designers do not take into consideration, the rotation of the flanges and the necessity for the flanges and the bolting to maintain a sufficiently high residual unit load on the gasket contact surface to contain internal pressure. These two conditions contribute to a vast majority of complaints on joint leakage. 3. The insistence of some inspection personnel that hydro static test conditions must be carried out at stress values for initial pretensioning of bolts at the allowable design stresses specified in the Code. Appendix S, in the Code, specifically covers this area and must be taken into cognizance anytime a hydrostatic test is to be performed. From a practical standpoint, when a flange is designed for pressure conditions of 600 psi and the hydrostatic test pressure is to be performed at 900 psi, it is obvious that a higher prestress must be applied to the bolts if a satisfactory test is to be applied. 4. The use of low yield bolting material, such as the austenitic stainless steels or ordinary carbon steel machine bolts. With both of these materials, it is relatively easy to stress the bolts beyond their yield point with eventual failure occurring using a standard wrench for the nominal bolt diameter. In order to successfully pass a hydrostatic test, it is often desirable and permissible to utilize a high strength alloy bolt for hydrostatic testing purposes. When this procedure is followed, the following steps are recommended: a. For hydrostatic testing, use ASTM B 193, Grade B 7 bolting materia], or equivalent, to initially seat the gasket and perform the hydrostatic test. b. After achieving a successful hydrostatic test, relieve the tension on the bolts to approximately 50% of the allowable boll stress and replace the bolts one at a time with the required bolting material. c. When replacement is made, the bolts should be stressed to the allowable stress for operating conditions. It should be pointed out a boll initially prestressed to 20,000 psi will very rapidly relax to approximately 50% of the initial applied stress due to creep and relaxation in the bolt material. Bolting that is stressed to 30,000 psi initially will relax to approximately 75% of its initial prest:ess over a short period of time. This indicates it is essential to prestress the bolt to a level that will guarantee maintenance of a stress level at operating conditions that will insure a safe joint. Thermal Expansion When bolis are initially prestressed to compensate for relaxation plus the usual hydrostatic end load, plus a residual gasket load, consideration must be given to stresses induced by thermal expansion under operating conditions. This can be caused by differential expansion of the flanges and the bolt material due to different coefficients of expansion or a temperature gradient that is present between the flange and the bolt material. In many installations, stresses developed by thermal expansion can adversely affect both the ability of the gasket to carry the applied forces and/or the ability of the bolt material to remain in an elastic state without being over-stressed. L. extreme cases, when thermal expansion is a serious problem and excessive bolt stresses or gasket loading can result, it may be practical for the gasket to be compressed only to a point that will permit further compression of the gasket as the loading due to thermal expansion is applied. In the case of a gasket with a compression stop, it may be practical to limit initial compression to within 8 to 10 thousandths of the final compressed range that is controlled by the thickness of the compression gauge ring or by the depth of the groove. By doing so, the build up of excessive stress in the bolts can be eliminated. In the case where a compression stop is not provided, the additional stresses can be absorbed by the gasket, providing the stresses re sulting from thermal expansion will not crush the gasket beyond its elastic limit. This is not a recommendation by FLEXITALLIC, but rather a suggestion to be considered in extreme cases by the designer. Developing Prestresses in Bolting* 1 The only completely satisfactory method for closing the flange and developing uniform stresses in each bolt at a controlled bolt stress is by measuring bolt elongation. This is an impractical approach, since the cost of bolting up using this procedure becomes excessive. An alternate means must be considered. The most frequent method is by utilizing torque wrenches. The use of torque wrenches, however, introduces many variables, and are not normally reliable methods of determining the actual bolt stress developed. Some of the factors that enter into the actual developed bolt stress are: 1. The class of fit of the bolt and nut 2. Presence of bum 3. The degree of lubrication achieved 4. The presence of grit, chips and dirt in the threads in the bolt and nut 5. Nicks 6. The relative condition of the seating surface on the flange against which the nut is rotated I cn co CO -Jo h-- CO , ' ' ; All of these variables have a marked effect on the amount of torque required to produce a given stress. Where conditions are fairly constant and reasonably controlled, it is possible to give nuts a certain torque value and obtain stresses that are consistent within reasonable limits. The required torque value can be obtained by tightening a sample bolt to a desired elongation while measuring the torque or by calculating it by means of formula. If this procedure is not followed, the actual developed stress in a stud can be completely unrealistic. Field tests have indicated that the use of torque wrenches in attempting to develop required bolt stresses can vary as much as 100% due to the variables present that have been previously mentioned. It is a requirement, particularly in the use of a FLEX1TALLIC gasket, that a reasonably, even compressive force, be applied. From a practical standpoint, in order to achieve this, a very definite bolt up procedure must be followed. This procedure is detailed as follows: 1. Install the gasket on the gasket seating surface and bring the cover flange in contact with the gasket. 2. Install all bolts, making sure they are free of dirt and grit, and are well lubricated. 3. Run up all nuts finger tight. 4. Develop the required bolt stress in a minimum of three steps, following a tightening up procedure as recommended in Sketch I. It is important to make certain that no more than 30% of the required bolt stress is achieved on the initial set. Should this occur, serious damage can be done to the FLEXITALLIC gasket and subsequent tightening can not offset the damage. After following this sequence a final tightening should be performed in a clockwise bolt to bolt sequence to assure all bolts have been evenly stressed. 653062 BOLTING UP SEQUENCE SKETCH I CONCLUSION I In summary, the FLEXITALLIC gasket is a carefully engineered, precisely made, quality product capable of providing industry with the optimum in closure sealing when used judiciously in accordance with good engineering practice. Beyond the horizon of today, FLEXITALLIC will maintain its leadership by providing for industry's needs as we face tomorrow's technological advances. The information contained in this bulletin is not to be taken as a warranty or representation for which we assume legal responsibility. It is offered solely for your consideration, investigation and verification. Comments, criticism and discussion on its contents are cordially invited. Please write, Flexitallic Gasket Co., Inc., P.O. Box 680, Camden, New Jersey 08101 U.S.A. or Flexitallic Gaskets Ltd., Station Lane, Heckmondwike, Yorkshire, EnglandT The authors are appreciative of the assistance freely given by their co-workers and others outside the company in preparing this bulletin and the extremely helpful suggestions and criticisms offered. CAUTION - We shall be under no liability tor loss, damage or injury incurred by any person and resulting directly or Indirectly from incorrect processing or use ot asbestos based products sold by us. In drawing your attention to the dangers to health from exposure to asbestos dust or fibers we would point out that most of our products containing asbestos fibers are produced with bonding agents, coatings or binders to render them safe for normal handling and usage. 13 390260 APPEND I* A CORROSIVES WHICH CAN INDUCE STRESS CORROSION CRACKING IN METALS Leigend: I - Intergranular Cracks T - Transgranular Cracks IT - Intergranular and/or Transgranular Cracks Ammonium Chloride Amines....................... Ammonia (pure) Ammonia (Dilute) . Ammonium Nitrate . IT T IT II Butane + Sulfur Dioxide.................................................... Cadmium................................................................................. Calcium Bromide............................................................... Chloride salts (see Inorganic and Organic Chlorides) Chromic Acid.......................................................................... Cresylic Acid (vapors)............... Cyanogen ......................................... Fluosilicic Acid........................... Hydrogen Chloride (some water) Hydrogen Cyanide (some water) Hydrogen sulfide (some water)............... Hydrofluoric Acid ......................................... ENOj , HC1, HF Pickling Acids............... Inorganic Chlorides (some water present) Inorganic Nitrates......................................... T T I I T (7) TT T IT IT T T I IT IT* a) j( ! Mercurous Nitrate ............................................................... Mercury..................................................................................... Meta) chlorides (see Inorganic chlorides) Mixed Acids (HaSO* + UNO,) .........................................i Nitrate salts (see Inorganic nitrates) 1 IT IT rr it Nitric Acid Manganese Chloride . . Nitric Acid (Red Fuming).......................... Nitric Acid (vapors) ................................. Oleum............................................................... Organic Chlorides (some water present) 1 T IT T 1 I <) Potassium Hydroxide Potassium Permanganate Salt Water + Oxygen . . Sillcofluoride Saltft . . Sodium hydroxide . . . 8team....................... Sulfate Liquor (white) Sulfide Liquor . . . , Sulfur Compounds . Oranyl Sulfate . . . . I I I ' IT IT I I i ()j< *> (5) (5) (6) T rr IT i (a) I (1) Acid attack oo steels containing martensite can cause cracking by hydrogen absorption in many media. ._ (2) Heating to temperature* of 475 C and above after exposure to sulfur compounds. (3) (vapor) (6) Stress Cracks Incooel, 1500 F. (4) (alloyed) (7) Stress Cracks MooeL (3) Stress Cracks SI- Bronze 400 F; Monel, 600 F. I CO --I o CO CO PO o APPENDIX B Ratmnttd from 1967 Corrosion Data Survey. NACE. 2*00 W. Loco S. Houitort. Tt. 77027 CORROSIVES WHICH INDUCE INTERGRANULAR CORROSION IN AUSTENITIC STAINLESS STEEL Acetic Wd Acetic Add + Stlicyfie Add Ammonium Nitrate Ammonium Sulfate Ammonium Sulfate + HtSO* Beet Juice Calcium Ni trate Chromic Add Chromium Chloride Copper Sulfate Crude 03 Fatty Adds Ferric Chloride Ferric Suffate Formic Add Hydrocyanic Add Hydrocyanic Add + Sulfur Dioxide Hydrofluoric Add + Ferric Sulfate Lactic Add Lactic Add + Nitric Add Maleic Add Nitric Add Nitric Add + Hydrochloric Add Nitric Add + Hydrofluoric Add Oxalic Add Phenol + Naphthenic Add Phosphoric Add PMheHc Add Salt Spray Sea Water Silver Nttnte + Acetic Add Sodium Bisulfate Sodium Hydroxide + Sodium Sulfide Sodium Hypochlorite Sulfite Cooking Liquor Sulfite Solution Sulfite Dfgester Add (Caldum Bisulfite + Sulfur Dioxide) Sulfamic Add Sulfur Di oxide (Wet) Sulfuric Add Sulfuric Add -f Acetic Add Sulfuric Add + Copper Sulfate Sulfuric Add 4- Ferrous Satiate Sulfuric Add + Methanol Sulfuric Acid 4- Nitric Add Sulfurous Add Water 4- Starch 4- Sulfur Dioxide Water 4 Aluminum Sulfate rsi r/ Cj --" -3- CD 1-- LO A w CHART NO. 2 BOLTING DATA FOR STANDARD FLANGES 1 NOMINAL PIPE SIZE (Inches) i '>* 1/2 3/4 1 1 1/4 1 1/2 2 2 1/2 ;3 , 31/2 !4 5 1! 6 8 10 12 14 16 18 20 24 150 PSI SERIES 300 PSI SERIES 400 PSI SERIES 1 600 PSI SERIES Diam. Diim. Diem. Diam. Diam. Diam. Diam. Oiam. of Nurvt* of Bolt of Nurrv of Bolt of Num~ of Bolt of Num- of Bolt Flange bar- of Bolts Circle Flange bar- of Bolts Circle Flange bar- of Bolts Circle Flange bar- of Bolts Circle (Inches) Bolts (Inches) (Inches) (Inches) Bolts (Inches) (Inches) (Inches) Bolts (Inches) (Inches) (Inches) Bolts (Inehas) (Inches! 3 3/8 3 1/2 4; 4! 1/2 2 1/4 1/2 2 3/8 3 3/8 1 4 3 3/4 1 4 3 7/8 4 1/2 2 3/4 4 5/8 : 4 4 1/4 4 1/2 3 1/8 4 7/8 4 1/2 2 1/4 3 3/8 . 4 1/2 2 5/8 3 3/4 i 4 5/8 3 1/4 4 5/8 4 5/8 3 1/2 4 7/8 4 1/2 | 1/2 1 5/8 5/8 2 1/4, 2 5/8! 3 1/4 3 1/2 3 3/8 i 3 3/4 1 4 5/8 4 7/8 4 4 4 4 1/2 2 1/4 1/2 2 5/8 5/8 3 1/4 5/8 3 1/2 4 5/8 5 6 7 4 4 4 4 1/2 3 1/2 1/2 3 7/8 5/8 4 3/4 5/8 5 1/2 5 1/4 6 1/8 6 1/2 7 1/2 4 4 8 8 5/8 3 7/8 5 1/4 4 3/4 4 1/2 6 1/8 4 5/8 5 6 1/2 , 8 3/4 5 7/8 7 1/2 8 5/8 3 7/8 5 1/4 4 3/4 4 1/2 6 1/8 4 5/8 5 6 1/2 8 3/4 5 7/8 7 1/2 8 5/8 3 7/8 3/4 4 1/2 5/8 5 3/4 5 7/8 7 1/2 8 1/2 9 10 4 8 8 8 5/8 6 8 1/4 8 5/8 7 9 8 5/8 7 1/2 10 3/4 8 1/2 11 iB 8 3/4 6 5/8 8 1/4 TTT 3/4 6 5/8 8 1/4 8 3/4 6 5/8 3/4 7 1/4 9 8 7/8 , 7 1/4 9 8 7/8 : 7 1/4 3/4 7 7/8 10 18 7/8 7 7/8 10 3/4 8 7/8 8 1/2 3/4 9 1/4 11 18 7/8 9 1/4 13 81 10 1/2 11 13 1/2 16 19 8 8 12 12 3/4 9 1/2 12 1/2 3/4 11 3/4 15 7/8 14 1/4 17 1/2 7/8 17 20 1/2 12 12 16 16 3/4 7/8 1 1 1/8 10 5/8 13 15 1/4 17 3/4 12 1/2 15 17 1/2 20 1/2 12 12 16 16 7/8 1 1 1/8 1 1/4 10 5/8 14 13 16 1/2 15 1/4 20 17 3/4 22 12 12 16 20 1 1 1/8 1 1/4 1 1/4 111/2 13 3/4 17 19 1/4 21 23 1/2 25 27 1/2 12 16 16 20 1 1 1 1/8 1 1/8 18 3/4 21 1/4 22 3/4 25 23 25 1/2 28 30 1/2 20 20 24 24 1 1/8 1 1/4 1 1/4 1 1/4 20 1/4 22 1/2 24 3/4 27 23 25 1/2 28 X 1/2 20 20 24 24 1 1/4 1 3/8 1 3/8 1 1/2 20 1/4 23 3/4 22 1/2 27 24 3/4 29 1/4 27 32 20 20 20 24 1 3/8 1 1/2 1 5/8 1 5/8 20 3/4 23 3/4 25 3/4 28 1/2 32 20 1 1/4 29 1/2 36 24 1 1/2 32 36 24 1 3/4 32 37 24 1 7/8 33 NOMINAL PIPE SIZE (Inches) 1 i Diam. of ! Flanga 1 (Inehas) ! 1/2 4 3/4 3/4 5 1/8 11 i 5 7/8 1 1/4 6 1/4 900 PSI SERIES Numbtr of Bolts Diam. of Bolts (Inehas) Bolt Circle (Inches) 4 3/4 . 3 1/4 4 3/4 3 1/2 4 7/8 4 4 7/8 4 3/8 Diam. of Flanga (Inehas) 4 3/4 5 1/8 5 7/8 6 1/4 1 1/2 i 7 !2 8 1/2 2 1/2 9 5/8 3 9 1/2 4 8i 8 8! 1 7/8 1 7/8 4 7/8 6 1/2 7 1/2 7 1/2 7 8 1/2 9 5/8 10 1/2 4 111/2 8 i 1 1/8 9 1/4 12 1/4 5 13 3/4 ; 8 1 1 1/4 , 11 14 3/4 6 15 ! 12 1 1 1/8 12 1/2 15 1/2 8 18 1/2 12 ! 1 3/8 15 1/2 19 10 21 1/2 16 1 3/8 18 1/2 23 12 24 ! 20 j 1 3/8 21 26 1/2 14 25 1/4 ; 20 1 1/2 22 29 1/2 16 27 3/4 20 1 5/8 24 1/4 32 1/2 18 31 20 1 7/8 27 36 20 33 3/4 20 2 29 1/2 38 3/4 24 41 20 2 1/2 35 1/2 46 1500 PSI SERIES Numbar of Bolts 4 4 4| 4 Diam. of Bolts (Inehas) 3/4 3/4 7/8 7/8 41 8 7/8 81 8 1 1/8 8 1 1/4 8 1 1/2 12 1 3/8 12 1 5/8 12 1 7/8 16 2 16 2 1/4 16 2 1/2 16 2 3/4 16 3 16 3 1/2 Bolt Cards (Inches) 3 1/4 3 1/2 " 4 3/8 Dtam. of I Flanga (Inehas) 5 1/4 5 1/2 . 6 1/4 7 1/4 4 7/8 6 1/2 7 1/2 8 8 9 1/4 10 1/2 12 9 1/2 111/2 | 12 1/2 i 15 1/2 : 14 16 1/2 19 21 3/4 19 22 1/2 25 27 3/4 26 1/2 30 2500PSI SERIES Number tt Bolts 4 4 4 4 Diam. of Bolts (Inches) 3/4 3/4 7/8 1 4 1 1/8 81 8 1 1/8 8 1 1/4 8 1 1/2 8 1 3/4 82 12 ' 2 12 2 1/2 12 2 3/4 X 1/2 32 3/4 39 Bolt Drde (Inches) 3 1/2 3 3/4 4 1/4 5 1/8 5 3/4 6 3/4 7 3/4 9 10 3/4 12 3/4 14 1/2 17 1/4 21 1/4 24 3/8 193069 STOUI 3322 Find it fast in the "Yellow Pages" under gaskets. There's a listing for your nearest Master Flexitallic Stocking Distributor in the Yellow Page Telephone Directory in more than 120 strategically located cities across the nation. 390262 9 ' <* FLEXITALLIC GASKET COMPANY INC Main Olllca A Factory: P.O. Box 680, Camden, New Jersey 06101 8 Linden Street. Camden, New Jersey 06102 Phone (609) 963-1130 Houston Plant: P.O. Box 760. Deer Park, Texas 77536 Phone (713) 479-3491 Lot Angeles Plant: . 602 Spruce Lake Drive Harbor city, California 90710 Phone (213) 549-7168 Main European Olllce A Factory: Flexitallic Qaaketa Limited Heckmondwike. Yorkshire. England. Telex 557465 Phone (0924) 405571 OTHER AFFILIATED COMPANIES In Australia. Mexico. Scotland. South Africa. Spain. New Zealand. Venezuela. West Germany 6L-1U0-SU