Search results for query: *

Hello, I have a nozzle with weight and operating loads: Weight forces = 1000 kN; Weight moments = 20000 kN*m Operating forces 1000 kN Operating moments = 30000 kN*n and I am using Nozzle Pro to check the stresses on nozzle shell junction by FEA. I added in the software loads as Operating only...

Hello everyone, I have a vessel NPS 26 with a nozzle NPS 18 where there are nozzle loads in the design combination with: - dead loads + seismic loads. The code is ASME VIII DIV.1 and with WRC 537 I checked dead loads and seismic loads as they would be separated load cases and then I used a Fea...

Thank you at all for the answers, I am trying to find a solution but the problem is on the corner. It is a vertical vessel and I don't need to use long. welds. Basically I will have plates size 4 ft x 6 ft connected with butt welds on the corner. I would want to use a butt weld corner joint and...

Hello guys, I am designing a pressure vessel with low pressure 15 psig but at high temperature 1025 °F in stainless steel 347H. It would be very easy if the vessel would be circular, but it is a rectangular vessel Size 4 ft x 6 ft. I started with 0.25 in but it seems to me the stress due to...

Hello everyone, I need to consider a load case with Nozzle Pro in order to verify a nozzle but I don't understand if the program can consider the load case combinations. For example if I have an operating weight + occasional load (the picture is only an example) how can the software combine...

I prefer to avoid appendix 46 and asme viii div 2. In the past, when we needed to follow U-2(g) I always used Fea analysis (nozzle pro for nozzles) to resolve the calculation. I checked the opening in div.1 and with fea analysis with allowables of div 1 I would check the nozzle. I have seen...

Hello, I have a nozzle with high loads that doesn't respect the ratio Rn/R and I need to follow U-2(g). In this case I have two options: Follow appendix 46 but in this case I need to use a very thick nozzle in order to verify primary stress; Follow ASME VIII div.1 with a thinner nozzle neck...

Hello, I solved the problem and I calculated adhesion pressure and contact pressure but what happens if the pressure used during expansion of the tubes is higher than the pressure where plastic deformation starts in the tubesheet?

Hello everyone, In the stress analysis due to nozzle loads with fea from the future I need to use Nozzle Pro program. Do you know if there are limitation with this program when we have thick cylinder or thick self reinforced nozzle? I can't modify mesh or finite element type with this...

Hello, I am studying tube - tubesheet connection during hydraulic expansion. I used Podohrsky book and I understood how to calculate the limiting pressure and adesion pressure but I don't understand how to calculate the pressure when tubesheet starts with plastic deformation. My idea is to use...

Design Code is ASME VIII div.1 at 20 barg

Good Morning, I need to do hydraulic test pressure (Stress results) on heat exchanger in corroded condition. In my case MAWP = Pdesign, but I can't activate in Compress the option to do the calculation in field corroded condition. (I have 3 mm of corrosion allowance for each component of the...

Thank you for your replies! In my case my mean metal temperature for shell side is 90°C and maximum operating shell side temperature is 120 °C so I am far from 175 °C or 185 °C required by design condition and I have temperatures for design case only. Unfortunately our client requires a...

Good evening, I am checking exchanger tubes in SB-111 061 C44300 under internal and external pressure with ASME VIII div.1. I have a internal design temperature of 100 °C and external design temperature of 185 °C. In accordance with ASME IID note G6, the maximum temperature for external pressure...

I wanted to know something more about 6*M/t^2 and I have always been kind. Next time you will see a question that for you is useless or without hope. Please don t answer. Regards

I have WRC 537 Last edition! Could you give me some advice please? I don't understand why 6*M/t^2 leads to an high stress due to bending moment. Many thanks for your help.

r6155 I used calculation by hand. I verified Nozzle Pipe and Shell thickness with Pressure and bending moments "distant" from nozzle-shell intersection and there are no problems: σ = P*D/2*t + ML*D/2*I + MC*D/2*I where D = external diameter (Pipe/Vessel) [mm] t = thickness (pipe/vessel) [mm] Mc...

Thank you for the reply TGS4 and I agree with you about stresses primary

Hello, I have a question about Nozzle Pro program. When I have to calculate a nozzle with FEA Analysis in the program

Hello, I am doing a replacement of existing item (heat exchanger AES type) and I have seen there is a number of tie rods lower than minimum required by TEMA for tube bundle. Which problem could we have if we don't respect minimum TEMA for tie rods? (we don't have to do thermal design) This is...