Embed Size px x x x x The following criteria apply for pumps with in. The forces contained herein areconsidered minimum criteria and should be adjustedwhere the vendor has experimental or test data permitting. The vendor must submit comparable cri-teria for pump cases constructed of cast hon. Suction and discharge nozzles should be designed towithstand forces and moments from the thermal expan-sion or contraction of prping. Themodulus of elasticity must be adjusted for the operatingtemperature condition.
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This document was uploaded by user and they confirmed that they have the permission to share it. If you are author or own the copyright of this book, please report to us by using this DMCA report form. Report DMCA. Home current Explore. Words: 44, Pages: Preview Full text. The vendor must submit comparable cri- teria for pump cases constructed of cast hon. Suction and discharge nozzles should be designed to withstand forces and moments from the thermal expansion or contraction of prping.
The forces contained herein are considered minimum criteria and should be adjusted where the vendor has experimental or test data permitting ANSI Code The modulus of elasticity must be adjusted for the operating temperature condition. Repinted courtes, of the Ameican Petroleum 25A Piping Stress Handbook neously to the pump through each nozzle, in addition to internal pressure, without causing an hternal rub or adversely affecting the operation of the pumps or seal.
The baseplate and pedestal support assembly should be adequate to limit the shaft displacement, when measured at the coupling, to a maximum of 0. These loads represent the total effect of all external mechanical forces that may be applied to a fully grouted pump base.
An algebraic surffnation should then be made for comparison with the moment limitation just given. The vendor should submit alternative criteria for pumps larger than 12 in. Because a particular nozzle on a pump will not always be subjected to the maximum allowable resultant force and moment simultaneously, an increase in either the resultant applied force or the resultant applied moment may be made if the following limitations can be satisfied at that nozzle:.
For heavy-duty baseplates the total applied resultant forces and moments on the suction and discharge nozzles should not be more than twice the eouivalent of those given in Thble For applied resultant forces and moments that are greater than these, allowable values shall be mutually agreed upon by the purchaser and the vendor. This limit is determined by the summation of the resultant applied force at the nozzle, lb resultant moment from Table , ft-lb resultant force from Table lb nominal diameter of nozzle flange.
The following criteria apply for pumps with 4-in. The forces contained herein are considered minimum criteria and should be adjusted where the vendor has experimental or test data permitting larger reactions.
Suction and discharge nozzles should be designed to withstand forces and moments from the thermal expan- sion or contraction of piping. Piping reactions shall be computed in conformance with the petroleum refinery piping code for pressure piping ANSI Code The modulus of elasticity should be adjusted for the operating temperature condition.
Pump coordinate system. Nominal Size of Nozzle Flange in. These loads represent the forces tliat may be applied to a ful1y grouted pump base. They are to be ap- tot;l effect of all externil mechanical 50D nozzle. An algebraic summation should then be made for comparison with the moment limitation just given.
The vendor must submit alternative criteria for pumps having a discharge flange of 4 in. It is suggested that these criteria be developed as a result of tests' F". Fra in tension 0. IpS or larger. The resultant shear force at the face of the flanee and any individual component may not exceed 2, lb. The resultant forces and individual components are limited The combined resultants of the forces and moments the centerlines of the exhaust connection and shaft must not exceed the following two conditions: 2s0 D.
The total resultant force and total resultant moment imposed on the turbine at any connection must not exceed the following: s0oD" where F : M: - Combined resultant of inlet. For values beyond this, use D. Components of these resultants should not exceed: D D o Resultant components: r - : o Individual comDonents: 1. M lb , including pressure forces where unrestrained exoansion joints are used at the connection.
The additional force referred to is perpendicular to the face of the exhaust flange and central. Use the larger of these two numbers for a vertical force component on exhaust connections in making the calculations just outlined. These values of allowable force and moment Dertain to the turbine structure only.
They do not pertain to the forces and moments in the cormecting piping, flange, and Design Criteria for Allowable Loads, Moments, and Stresses flange bolting that should not exceed the allowable stress as defined by applicable codes and regulatory bodies.
See Figure IPS or larger. The resultant shear force at the face of the flange and anv individual component should not exceed lb. The operating and installed conditions. The total resultant force and total resultant moment imposed on the turbine at any connection must not exceed the following: F s00D.
Turbine coordinate system. Combined resultant of suction, interstage and discharge forces, lb Combined resultant of suction, interstage and discharge moments result- ing from forces, ftlb Diameter in. Resultant moment, ftlb Pipe size of the connection IPS up to 8 inches in diameter. The combined resultants of the forces and moments of the suction interstage and discharge connections, resolved at the centerlines of the discharge comection must not exceed the followins two conditions.
The resultant shear force at the face of the flanee and any individual component should not exceed 2,60 lb. The resultant forces and individual components will be limited further as follows: r M J D: At the operating temperature, using the hot modulus "8," resultant bending moments are permissible up to a - D.
Components of these resultants should not exceed: F," Fy. F,, 92 D. The resultant shear force at the face of the flange and any individual component shall not exceed lb. The re-. ComDonents of these resultants should not exceed: F. The total resultant force and total resultant moment imposed on the turbine at any connection must not exceed the followins: F s00D" - M Each nozzle in the corroded condition must be capable of withstanding the moments and forces defined in Table The design of each fixed header, of the fixed header to sideframe connection, and of other support members should be such that no damage will occur due to the simul- Piping Stress Handbook taneous application of the following design iotal nozzle loadings on a single header: For the direction of loads see Figure The total of all nozzle loads on one multibundle bav should not exceed three times that allowed for a singli header.
Reproduced lrcm Air-Cooled Heat Simptified Solutions for Pipe Stress These tables are developed as a tool for the piping stress can readily be seen that the smaller expansion engineer or the piping designer by which he can quickly evaluate a proposed layout before he proceeds with his deslgn worK.
It is important for the reader to understand that the tables presented herein do not compose a rigorous solution to the pipe stress problem. Computer calculations must be made for borderline cases. The tables are approximate values onlv for two-anchor oroblems. Example Problem Consider the piping arrangement in Figure Size: 8 in.
Schedule: Sch 40 Material: O. By inspection, it will deflect the longer leg more easily than the larger expansion will the shorter leg. To develop Tables and , a guided cantilever formula has been used to calculate stresses. If we observe our Example Problem for an expansion ofX in.
If Point A is attached to a piece of rotating equipment, you will need to have about 23 ft to make the system more flexible. If the system is attached to a piece of nonrotating equipment, a ft offset will be sufficient. To find the thermal forces Table is to be used, which shows forces for a unit reflection with various leneths of offset. Note that in identifuing pipe sizes the tables show wall thickness and moment of inertia as well as O.
Diagram for Example Problem 6,lb. Text continued on page T 2S I 4S I 15 Required to Absorb Expansion A in. L 78,5 82,8 I I2A. S lg ti;? S 1,39? S: ?
S75 t? S16 l! I5 lJ. S6t ES t9,-1S5 59! S1: E4d 19,? Eiri 13, Sl. S llrl75 i. F87 t,3lg 5. Il9 i 4, l.
I,:a: 4,78 t i,9! D it5 7.
Piping Stress Handbook - by Victor Helguero - Part 2.pdf
Piping Stress Handbook - By Victor Helguero - Part 1
Piping Stress Handbook - By Victor Helguero - Part 2.pdf