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e between adjacent convolutions of 7% after the pressure test required by NE-6230. (c) The ratio of the internal pressure at which the bel- lows will become unstable (squirm) to the equivalent cold service astm download pressure shall exceed 2.25. By definition, squirm shall be considered to have occurred if under internal pres- sure an initially symmetrical bellows deforms, resulting in a lack of parallelism or uneven spacing of adjacent convolutions at any point on the circumference. Unless otherwise specified, this deformation shall be construed as unacceptable squirm when the ratio of the maximum convolution pitch under internal pressure exceeds 1.15 for unreinforced and 1.20 for reinforced bellows. In the case of universal expansion joints, which consist of two bellows joined by a cylindrical section, compliance ansi/astm pdf with these crite- ria shall be satisfied by the entire assembly. No external restraints on the bellows shall be employed during squirm testing other than those which will exist after installation. (1) For single joints used in axial or lateral motion, the squirm test may be performed with the bellows fixed in the straight position at the maximum length expected in service; for rotation and universal joints, the bellows shall be held at the maximum design rotation angle or offset movement. In the case of single joints subjected to rotation movement, or of universal joints subjected to lat- eral offset movement, an instability condition as previously defined may or may not appear. Instead, movement of the convolutions may occur due to the superposition of the lateral internal pressure component on the applied rotation.

In such cases, that portion of the bellows deformation due to the design rotation angle or offset movement shall not be included in the deformation used to define squirm. (2) In the case of squirm tests, the equivalent cold service pressure is de fined as the Design Pressure multiplied by the ratio Ec fi Eh, where Ec and Eh are defined 17 For general information, see standards of the Expansion Joint Manu- as the modulus of elasticity of the bellows material at room facturers Association, Inc., 25 N. Broa e between adjacent convolutions of 7% after the pressure test required by NE-6230. (c) The ratio of the internal pressure at which the bel- lows will become unstable (squirm) to the equivalent cold service pressure shall exceed 2.25. By definition, squirm shall be considered to have occurred if under internal pres- sure an initially symmetrical bellows deforms, resulting in a lack of parallelism or uneven spacing of adjacent convolutions at any point on the circumference. Unless otherwise specified, this deformation shall be construed as unacceptable squirm when the ratio of the maximum convolution pitch under internal pressure exceeds 1.15 for unreinforced and 1.20 for reinforced bellows. In the case of universal expansion joints, which consist of two bellows joined by a cylindrical section, compliance with these crite- ria shall be satisfied by the entire assembly. No external restraints on the bellows shall be employed during squirm testing other than those which will exist after installation. (1) For single joints used in axial or lateral motion, the squirm test may be performed with the bellows fixed in the straight position at the maximum length expected in service; for rotation and universal joints, the bellows shall be held at the maximum design rotation angle or offset movement. In the case of single joints subjected to rotation movement, or of universal joints subjected to lat- eral offset movement, an instability condition as previously defined may or may not appear. Instead, movement of the convolutions may occur due to the superposition of the lateral internal pressure component on the applied rotation. In such cases, that portion of the bellows deformation due to the design rotation angle or offset movement shall not be included in the deformation used to define squirm. (2) In the case of squirm tests, the equivalent cold service pressure is de fined as the Design Pressure multiplied by the ratio Ec astm a53 fi Eh, where Ec and Eh are defined For general information, see standards of the Expansion Joint Manu- as the modulus of elasticity of the bellows material at room facturers Association, Inc., 25 N. Broa

given in relation to fatigue analysis based on fatigue tests and fracture mechanics. Reference is made to Annex C for practical details with respect to fatigue design. The aim of the fatigue design is to ensure that the C/WO riser has an adequate fatigue life. Calculated fatigue lives can form the basis for a fatigue crack inspection programme during fabrication and the service life of the C/WO riser. All cyclic load effects imposed during the entire life that have magnitude and number large enough to induce significant fatigue damage effect shall be taken into account; see 6.3.4.4. All modes of operation, including open-sea mode and tubing hanger mode (inside marine riser) and temporary conditions like running and hang-off, should be considered.

As a minimum, fatigue analysis shall be performed in connected conditions for open-sea mode and tubing hanger mode (operation inside marine riser) when appropriate. 97 (c) ISO 2005 - All rights reserved 97 ISO 13628-7:2005(E) Recommended Practice 17G / ISO 13628-7 C/WO risers should be designed so that vortex-induced resonant vibrations are prevented, whenever practical. Vortex suppression devices may be used as a method to minimize the strength of vortex-induced resonant vibrations; for further details, see API RP 2RD [2]. Fatigue-sensitive points shall be identified and a fatigue analysis shall be performed asme pdf for each point. Emphasis should be on bolts, welds and details with stress concentrations, in addition to locations with high surface roughness and surface marks. If there is a significant risk of fatigue failure, the design should be reviewed to reduce the risk by considering changes to the configuration to lower peak stresses, e.g. by reducing girth weld eccentricities, the provision of smooth profiles, particularly at welds, and the use of less susceptible materials. The fatigue life may be calculated by methods based on cumulative damage and/or crack growth analysis. Normally, the methods based on cumulative damage should be used during asme pdf design for fatigue life assessment due to its simplicity and efficienc

It is advisable to perform the work so there is no possibility of the crane, load line, or load becoming a conductive path. [See Fig. 22-3.3.2.1-1, illus- trations (a) and (b).] Cranes shall not be used to handle materials stored under electric power lines unless any combination of boom, load, load line, or machine com- ponent cannot enter the prohibited zone. Operating articulating boom cranes where they can become electri- fied with electric power lines is not recommended, unless there is no less hazardous way to perform the job. Any overhead line shall be considered to be an ener- gized line, unless and until the person owning such line or the electrical utility authorities, indicate that it is not an energized line.

Crane operators shall not rely on the coverings of lines for their protection. Four conditions to consider when operating an articulating boom crane near electric asme bpvc section viii power lines are the following: (a) power lines de-energized and grounded as in para. 22-3.3.2.2 (b) power lines energized, crane operating less than the erected/fully extended boom length away as in para. 22-3.3.2.3 [see Fig. 22-3.3.2.1-1, illustration (c)] (c) power lines energized, crane within prohibited zone as in para. 22-3.3.2.4 (d) crane in transit, no load, and boom lowered as in para. 22-3.2.3.5 22-3.3.2.2 Crane Operation Near De-Energized and Grounded Electric Power Lines. This is the preferred condition under which the operation can be performed. The hazard of w3.org injury or death due to electrocution has been removed. The following steps shall be taken to ensure de-energization of the power lines: (a) The power company or owner of the power lines shall de-energize the lines. (b) The lines shall be visibly grounded to avoid electri- cal feedback and appropriately marked at job site location. (c) The necessity for grounding of wiring that has a manufacturer's applied coating of insulation and is a 600-V service or less shall be determined by electrical utilities or the owner of the power line. (d) A qualified representative of the owner of the lines or a designated representative of the electrical utility shall be on the site to ver

Full thread engagement Eye Jaw Nut Open body with Pipe body with jaw and eye fittings hook and eye fittings Open body Installation Loading With Nuts Pipe body Types Components Fig. 26-2.1.1-2 Eyebolts 6 deg-15 deg (10) 16 deg- 90 deg 0 deg- 5 deg Nonshoulder machinery Nonshoulder nut Shoulder machinery Shoulder nut Tapped blind hole Tapped Untapped through hole through hole Installation Angular Loading In-line loading only Types 9 Loading ASME asme bpvc section viii B30.26-2010 Fig. 26-2.1.1-3 Eye Nuts Through hole no nut Typical Types Through hole top nut Through hole bottom nut Installation 10 In-line loading only Loading ASME B30.26-2010 Fig. 26-2.1.1-4 Swivel Hoist Rings Bail Bolt Swivel bushing Pin Bushing flange

(10) Side pull swivel hoist ring Bail swivel hoist ring Tapped hole Components Full pivot 360-deg rotation Chain swivel Webbing swivel 100% loading hoist ring hoist ring Through hole at any direction or angle in-line with bail Types Installation 11 Loading ASME B30.26-2010 26-2.6.2 Chemically Active Environments THE STRENGTH OF ADJUSTABLE HARDWARE CAN BE AFFECTED BY CHEMICALLY ACTIVE ENVIRONMENTS SUCH AS CAUSTIC OR ACID SUBSTANCES OR FUMES. THE ADJUSTABLE HARDWARE MAN- UFACTURER OR A QUALIFIED PERSON SHOULD BE CONSULTED BEFORE USE IN CHEMICALLY ACTIVE ENVIRONMENTS. SECTION 26-2.7: TRAINING ADJUSTABLE HARDWARE USERS SHALL BE TRAINED IN THE SELECTION, INSPECTION, CAUTIONS TO PERSONNEL, EFFECTS OF ENVIRONMENT, aol.com AND RIGGING PRACTICE

e releasing carrier, passing over and driving the governor sheave, and providing continuous information on the speed and direction of the car or counterweight. rope, safety drum (also known as "Tail rope" and "Minne Line"): a corrosion-resistant wire rope used to connect the governor rope to the safety. Primarily used with wedge clamp safeties. rope, suspension (hoisting): wire rope used to raise and lower an elevator, dumbwaiter, or material lift car or its counterweight, or both. rope equalizer, suspension: a device installed on an elevator, dumbwaiter, or material lift car or counter- weight to equalize automatically the tensions in the sus- pension wire ropes.

rope-fastening device, auxiliary: a device attached to the car or counterweight or to the overhead dead-end rope-hitch support that will function automatically to support the car or counterweight in case the regular 15 wire rope fastening fails at the point of connection to the car or counterweight or at the overhead dead-end hitch. rope sprocket UL pdf download drive: a driving means consisting of wire rope with fixed links at constant intervals throughout its length. The links engage in slots on a grooved drive cog to provide a positive drive force. runby, bottom, elevator car: the distance between the car buffer striker plate and the striking surface of the car buffer when the car floor is level with the bottom terminal landing. runby, bottom, elevator counterweight: the distance between the counterweight buffer striker plate and the striking surface of the counterweight buffer when the car floor is level with the top terminal landing. runby, top, direct-plunger hydraulic elevator:download UL pdf the dis- tance the elevator car can run above its top terminal landing before the plunger strikes its mechanical stop. running gear, escalator: all the components of an escala- tor moving along the tracks. running gear, moving walk: all the components of a moving walk moving along the tracks. safety, car or counterweight: a mechanical device attached t

vature of the external contoured portion of the outlet, i.e., hofi�� ro. See nomenclature and Fig. 404.3.1(b)(3). (b) These rules do not apply to any nozzle in which additional nonintegral material is applied in the form of rings, pads, or saddles. (c) These rules apply only to cases where the axis of the outlet intersects and is perpendicular to the axis of the header. (4) Notation. The notation used herein is illustrated in Fig. 404.3.1(b)(3). All dimensions are in inches (mm). D p outside diameter of header Dc p internal diameter of header Do p internal diameter of extruded outlet measured at the level of the outside surface of header d p outside diameter of branch pipe dc p internal diameter of branch pipe ho p height of the extruded lip. This must be equal to or greater than ro except as shown in para. 404.3.1(b)(4)(b) below. L p height of the reinforcement zone p 0.7 dTo r1 p half-width of reinforcement zone (equal to Do) ro p radius of curvature of external contoured por- tion of outlet measured in the plane containing the axes of the header and branch. This is sub- ject to the following limitations.

(a) Minimum Radius. This dimension shall not be less than 0.05d, except that on branch diameters larger than NPS 30 it need not exceed 1.50 in. (38 mm). (b) Maximum Radius. For outlet pipe sizes NPS 8 and larger, this dimension shall not exceed 0.10d + 0.50 in. (13 mm). For outlet pipe sizes less UL download than NPS 8, this dimension shall not be greater than 1.25 in. (32 mm). (c) When the external contour contains more than one radius, UL download the radius of any arc sector of approximately 45 deg shall meet the require- ments of paras. 404.3.1(b)(4)(a) and (b) above. (d) Machining shall not be employed in order to meet the above requirements. Tb p actual nominal wall thickness of branch Th p actual nominal wall thickness of header To p finished thickness of extruded outlet sured at a height equal to ro above the outside surface of the header tb p required thickness of the branch pipe according to the wall thickness equation in para. 404.1.2 th p required thickness of the header according to the wall thickness equation in para.

extensive changes in the code than could be provided by supplements alone. The decision was reached by the American Standards Association and the sponsor to reorganize the Sectional Committee and its several subcommittees, UL download and to invite the various interested bodies to reaffirm their representatives or to designate new ones. Following asme pdf its reorganization, Sectional Committee B31 made an intensive review of the 1942 code, and a revised code was approved and published in February 1951 with the designation ASA B31.1-1951, which included: (a) a general revision and extension of requirements to agree with practices current at the time; (b) revision of references to existing dimensional standards and material specifications, and the addition of references to new ones; and (c) clarification of ambiguous or conflicting requirements. Supplement No. 1 to B31.1 was approved and published in 1953 as ASA B31.1a-1953. This Supplement and other approved revisions were included in a new edition of B31.1 published in 1955 with the designation ASA B31.1-1955.

A review by B31 Executive and Sectional Committees in 1955 resulted in a decision to develop and publish industry sections as separate code documents of the American Standard B31 Code for Pressure Piping. ASA B31.4-1959 was the first separate code document for Oil Transportation Piping Systems and superseded that part of Section 3 of the B31.1-1955 code covering Oil Transpor- tation Piping Systems. In 1966 B31.4 was revised to expand coverage on welding, inspection, and testing, and to add new chapters covering construction requirements and operation and maintenance procedures affecting the safety of the piping systems. This revision was published with the designation USAS B31.4-1966, Liquid Petroleum Transportation Piping Systems, since the American Standards Association was reconstituted as the United States of America Standards Institute in 1966. The United States of America Standards Institute, Inc., changed its name, effective October 6, 1969, to the American National Standards Institute, Inc., and USAS B31.4-1966 was redesignated as ANSI B31.4-1966. The B31 Sectional Committee was redesignated

s and annulments, then appear in the next update. As of the 1992 and later editions, all Cases currently in effect at the time of publication of an edition are included with it as an update. The ASME B31 Code for Pressure Piping Standards Committee took action to eliminate Code Case expiration asme pdf dates effective September 21, 2007. This means that all Code Cases listed in this update and beyond will remain available for use until annulled by the ASME B31 Code for Pressure Piping Standards Committee. This update, Cases No. 33, which is included after the last page of the 2008 Addenda and the Interpretations Volume 43 that follow, contains the following Cases: 175 176 177 179 182 183 The page numbers for the Cases supplements included with updates to the 2007 Edition start with C-1 and will continue consecutively through the last update to this Edition.

The Cases affected by this supplement are as follows: Page C-15 C-17 C-19 C-20 C-21 C-23 Location Case 175 Case 176 Case 177 Case 179 Case 182 CaseChange Expiration date eliminated Expiration date eliminated Expiration date eliminated Expiration date eliminated Expiration date eliminated Expiration date eliminated INTENTIONALLY LEFT BLANK ASME B31.1 CASES B31 CASE 175 ASTM B 16 (UNS C36000) and B 453 (UNS C35300) in ASME B31.1 Construction Approval Date: September 12, 2003 Reaffirmation Date: August 7, 2007 Inquiry: May brass alloys rods and bars conforming to ASTM B 16 (UNS C36000) and B 453 (UNS C35300) be used for ASME asme pdf B31.1 constructionfi Reply: It is the opinion of the Committee that brass alloys rods and bars conforming to ASTM B 16 (UNS C36000) and B 453 (UNS C35300) may be used for B31.1 construction provided: (a) These materials shall not be used for boiler exter- nal piping except where specifically permitted by Section I. See para. 100.1.2(A). (b) The maximum permissible design temperature shall not exceed 406

omponent design limit. Examples of component design limits are as follows: (a) a requirement that a single heat exchanger was 9 ACCEPTANCE CRITERIA Acceptance criteria consists of the following three designed to transfer a specific amount of heat (b) a requirement that a single heat exchanger was designed for operating with a specified pressure drop types of limits: 178 ASME OM-2009 PART 21 (STANDARDS) 9.3 Required Action Limits Required action limits shall be established for each heat exchanger to allow corrective action to be taken prior to exceeding the system asme pdf operability limit. Required action limits are based on the known fouling (or other degradation) rate, as determined by parameter trending (see para. 6.10), after applying a 95% confidence level to the data. This 95% confidence level is determined based on the total uncertainty calculated for the test or monitoring result (see section 8 and Fig. 1). Required action limits shall be used to ensure heat occurred more rapidly than expected, then other heat exchangers should be evaluated according to the follow- ing priority:

(a) Evaluate those heat exchangers that are known to have the least margin.

(b) Evaluate those heat exchangers that are asme pdf likely to have been subject to the same fouling (or degradation) mechanism.

(c) Evaluate those heat exchangers that are next on the existing schedule. exchanger operational readiness throughout the entire 11 RECORDS AND RECORD KEEPING interval of testing or monitoring (see para. 5.4). 11.1 Equipment Records 10 CORRECTIVE ACTION A record shall be maintained that contains the follow- ing information for each heat exchanger covered here: Corrective action (flushing, mechanical cleaning, chemical cleaning, mechanical repair, etc.) shall be per- formed following failure to meet the acceptance criteria as defined in section 9, or whenever I (test) exceeds I (max.), as described in Fig. 1. As part of this corrective action, the root cause of the failure should be determined (see Nonmandatory Appendix A of this Part). Unless the effectiveness of the corrective action

(a) 0.002 in. for nominal asme bavc pdf wrench openings 3fi16 in. to 1 in. (b) 0.003 in. for nominal wrench openings 11fi16 in. to 1 (c) 0.004 in. for nominal wrench openings 25fi16 in. to 1 5.3 Alternative Coating Test This test consists of an adhesion, abrasion, and corro- sion test specified in paras. 5.3.2, 5.3.3, and 5.3.4. 5.3.1 Test Preparation. The quantity and condition 5.3.2 Adhesion Test. Test specimens shall pass the file or grind-saw test of ASTM B 571. 5.3.3 Abrasion Test. Test specimens shall have no base material exposed after being subjected to 100 L of falling sand per ASTM D 968 Method A. 5.3.4 Corrosion Test. Test specimens shall be tested for UL pdf corrosion resistance by exposure to a 48 hr salt spray test, as specified in ASTM B 117, without falling below the ASTM B 537 rating of 6. of the wrenches used for the following testi

shall be 6 DESIGNATIONS per the manufacturer's standard practice or as mutually agreed to by the manufacturer and the customer. If the wrench does not have sufficient surface area to conduct the tests, a 3fi4 in. combination wrench, or a 4 in. x 6 in. panel(s) per ASTM B 537/ASTM D 968 Method A, shall be used. 29 Wrenches shall be designated by the following data in the sequence shown: type, class, size of drive, size and type of openings (6- or 12-point), and coating. EXAMPLE: Wrench Type I crowfoot wrench, flare nut, Class 2, heavy duty, 3fi8 in. square drive, 1fi2 in. 12-point opening, black oxide. ASME B107.100-2010 (B107.21) Table 3 Type I, Class 1, Flare Nut, 1fi2 in. Square Drive, Standard Duty Dimensions, in. Slot Head Head Drive End Center Drive Square Drive End Minimum Thickness.