Jacketed Vessel Design (design of dimple jackets) Jacketed Vessel Design (design of dimple jackets) The design of dimple jackets permits construction from light gauge metals without sacrificing the strength required to withstand the specified pressure. This results in considerable cost saving as compared to convention jackets. Desi gn calculation begin with an assumed flow velocity between 2 and 5 ft/s. As a rule of thumb the jacket pressure will be governing when internal pressure of vessel is less than 1.67 times the jacket pressure. At such conditions, dimple jackets are typically more economical than other choices. However in small vessels (less than 10 gallons) it is not practical to apply dimple jackets. The design of dimple jackets is governed by the National Board of Boiler and Pressure Vessel Inspectors and can be stamped sta mped in accordance with ASME Unfired Pressure Vessel Code. Dimple jackets are limited to a pressure of 300 psi by Section VIII, Div.I of the ASME Code. The design temperature is limited to 700 °F. At high temperatures, it is mandatory that jacket be fabricated from a metal having same thermal coefficient of expansion as that used in inner vessel.
Heat Transfer Coefficients: Dimple Jackets Click here to view the full size image !!!
All other variables are as previously defined. Garvin (CEP Magazine, April 2001) reports an average error of 9.8% with manufacturers data for the above correlation and a maximum error of 30% over 116 data points. This results in average deviations i n the heat transfer coefficient of 15-20% most of which was at velocities below 2 ft/s. Good agreement with manufacturers data was found between 3 and 6 ft/ s. A recommended excess area of 15% should be used in this velocit y range. Note: The correlation above is for integrally welded jackets (ie. jackets welded directly to the vessel). If a dimple jacket is clamped onto an existing vessel and adhered with heat transfer mastic, the overall heat transfer coefficient of the system will be very low. Mastic is used to try to minimize air pocket resistances between the vessel wall and the jacket. Historically, this arrangement results in poor heat transfer. A recommended overall heat transfer coefficient of 10-15 Btu/h ft² °F should be used for such systems regardless of the utility used. Pressure Drop: Dimple Jackets The pressure loss in a dimple jacket can be estimated from the following for water or water-like fluids: Pressure Loss in Jacket = (Total Lenght of Flow, ft) x ((0.40 x Velocity, ft/s) - 0.35) Pressure Loss Across Entire Jacket (including inlets and outlets) = Pressure Loss in Jacket + (0.10)(Pressure Loss in Jacket) The above estimates should be used for velocities ranging from 1.5 to 6 ft/ s. This method is based on a graph found on page 217 of the Encyclopedia of Pharmaceutical Technology by James Swarbrick. For detailed design, it is advisable to rel y on manufacturer's data for pressure drop calculations. Heat Transfer Coefficients Inside Agitated Process Vessels
In order to complete the overall heat transfer coefficient calculation, an estimate must also be made inside the process vessel. The following estimate should yield reasonable
results:
Click here to view the full size image !!!
Calculating the Overall Heat Transfer Coefficient When calculating the overall heat transfer coefficient for a system, the vessel wall resistance and any jacket fouling must be taken int o account:
Notice that the thermal conducitivity of the vessel wall and the wall thickness are included in the calculation. A typical jacket fouling factor is around 0.001 h ft² °F/Btu. When calculating the overall heat transfer coefficient, use a "common sense" analysis of the final value. The table below will give some guidance to reasonable final values: English Units Click here to view the full size image !!!
