Horizontal Retention Vessel
File: Samples/Sample 3, Last Updated: Sept 13 2016, Laurence Brundrett
This sample is based on a real vessel. The operating conditions and dimensions have been altered.
This 8ft diameter contact tank (or retention vessel) keeps water and chlorine in contact for a guaranteed minimum safe amount of time at the maximum possible flow rate. A longer contact time (with reduced pressure vessel volume) is achieved by providing a serpentine flow path (this can be seen in the drawings). The baffles prevent short circuiting of the flow from the input to output.
Usually a tank in this service does not need to be code stamped. This vessel was designed and built to ASME VIII-1 per the customer’s specification but not registered.
Flexible Saddles and Saddle Design:
Per ASME VIII-1 appendix G-l:
A vessel supported in a vertical or horizontal position will have concentrated loads imposed on the shell where the supports are attached… Calculations to resist the forces involved are not given here because they involve so many variables depending upon the size and weight of vessels, the temperature of service, the internal pressure, the arrangement of the supporting structure, and the piping attached to the vessel as installed.
Saddles for horizontal tanks are usually designed based on the work of L.P. Zick “Stresses in Large Horizontal Cylindrical Pressure Vessels on Two Saddle Supports” first published in September 1951 “THE WELDING JOURNAL RESEARCH SUPPLEMENT.” http://www.codeware.com/support/papers/zick.pdf
The good news about the Zick analysis is that it calculates all of the support stresses that are required to design a horizontal vessel. Most commercial programs include the Zick analysis making it easy to perform.
- The beam bending stresses (S1) in the vessel are calculated at the midpoint and over the saddles. These are standard beam bending methods. Tension stresses include shell pressurization stresses, compression stresses are calculated unpressurized. Long small diameter vessels can have significant bending stresses.
- Tangential Shear in shell and head at the plane of the saddle (S2). This tangential stress is rarely significant.
- Circumferential Stress at the Horn of the Saddle and at the end of the wear plate (S3). These are often the most important stresses.
- Additional Stresses in Head Used as a Stiffener (S4). Not usually significant.
- Ring Compression in the Shell Over the Saddle (S5)
The bad news about the Zick analysis is that it usually underestimates the peak stress in the saddle horn, often by a factor of 2 or more. Zick analysis is based on the use of design factors based on minimum research on a narrow range of geometry, and seldom matches the results found from Finite Element Analysis. Real stresses in vessels with large diameters and thin walls can be high enough to reduce the long-term cycle life of a vessel. A simple check is to assume that Zick underestimates the true saddle horn stress (S3) by 3x. For many small or thick walled vessels this is not a problem. This 8ft vessel has a S3 less than 1/3 the allowed limit so additional analysis is not required (See R3 in the sample calculations saddle section, page 35 of 38). In addition, this flexible saddle design further reduces the horn stress beyond the geometries studied by Zick.
This sample has been calculated using Design Calcs. For a larger diameter or thinner shell where S3 gets closer to the allowed limits, additional analysis of the shell to saddle zone would be justified.
More Information on Flexible Saddles (External Links):
- The Support of Horizontal Vessels Containing High-Temperature Fluids A Design Study
- Peak Stress and Fatigue Assessment at the Saddle Support of a Cylindrical Vessel
Downloads (pdf Format):
We work to many ASME standards to design and validate pressure vessels, boiler, fittings and piping systems. We have experience designing thousands of vessels and fittings to multiple codes.
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