It is clear from your post that the steam side steam pressure will not exceed the safety limits of the heater. So the steam side safety valve is not required.
Even then a shell side relief will be required. Consider the case when some of the tubes are ruptured. The tube side pressure will be...
In a normal thermal power plant, there is no PCV, and the heating steam sources are uncontrolled extraction points from the steam turbine. On the other hand, for PRV sizing, we used to follow the HEI code.
In your case, you are using a controlled external steam source. As per ASME code, in...
The factor of 1.25 allowed for cyclic thermal loads and 1.2 for occasional loads(B31.1) because these loads are transitory in nature, whereas the sustained load is continuous. As per ASME codes it is allowable to exceed the allowable stress for short periods.
But at low temperature...
It appears this is a huge fan with 302 mm H2O fan head.
TLT fans is a company supplying FD/ID fans for coal power plants which look similar in size and rating.
Howden is another company.
As per table 323.2.2A, up to a thickness of 12.7 mm -55 deg F minimum temperature can be used without impact testing.
For higher thicknesses, both table 323.2.2A and 323.2.2B can be used, in my opinion. The most restrictive minimum temperature should be used for obviating impact tests.
For...
The B31.1 force calculation does not require the flow to be supersonic.
However, as per the same B 31.1 document, the designer has the responsibility to ensure that the results are conservative.
There is a major deviation of your system from the usual safety valve configuration. The...
The paper I cited was authored by P. K. Swamee, who formulated the famous Swamee-Jain friction factor formula.
I have done a preliminary calculation based on your data and above reference as below:
Disclaimer: Please check with your own past experience and reference above before using the same.
1. Since Cat A is not mentioned for angle joints, angle joints can not be used for Cat A welds.
2. Try Non-Mandatory Appendix L for joint efficiencies.
There is a book titled Fatigue of Structures and Materials by Jaap Schijve where a chapter is devoted to corrosion fatigue. You will also get a number of references to published papers there on this subject.
Since the pressure is 50 psig>15 psig, the HEX should fall within the scope of Sec VIII-1. Refer TEMA Clause RCB 1.13, where this requirement is mentioned.
The subclause you mentioned refers to accumulators, which are excluded if they are within limits. However, if within limits, they can be...
Assuming P=1480 psi, D=28 in, E=1, S=0.72x65000x1=46800 psi,
Min thickness t=(PD/2S)=0.443 in. for pipes
Considering a manufacturing tolerance of 12.5%, the minimum thickness should be 0.443/0.875=0.506 in.
On top of this, you need to add corrosion allowance A as per industry practice.
So...
Which thickness are you talking about regarding flange? 1/2 in flange thickness is grossly in error. For 24 in 600 lb rating flange, the minimum flange thickness (C) is 4 in, as per B 16.5. However, please check the latest code.
If the minimum thickness is as per code, there is no need to increase the thickness to take care of the hydrotest pressure. In fact, it is the other way round. You need to reduce the test pressure in case certain stress values under test conditions exceed the criteria given in Cl 345.2.1 (a) of...
Your data are obscure.
1. Is it a closed discharge or open discharge (i.e., whether the discharge elbow is decoupled from the vent pipe)?
2. How did you arrive at P2 = 7.65 bar(g)? This should be calculated after calculating pressure drops across all equipment, fittings, and piping downstream...
