Nozzle calculation according to API 610

Hello,

I’m working on HP Pump replacement for a LNG project in France.
We must verify that the forces and moments at the nozzle are lower than the allowable ones, according to table 4 of API 610.
I’m using the API 610 module of CAESAR II R1 :

1)Can someone describe me the exact meaning of “top”/”end”/”side” nozzle ? Which of these should I take ? (Image of the pump is attached on top)

2)The pump that I try to implement is not a “vertical in-line pump” isn’t it ? So I have to fill the nozzle location DX, DY, DZ.

But I cannot define the base point of my pump, because you’ll see on the figure that the intersection between the pump shaft centerline and the vertical plane passing through the center of the two pedestals does not creating a “point”…

Could you please tell me how to define the base point ?


Thanks a lot.
[img:right]http://hpics.li/b4af11f[/img]

Dear Bongo,

As per my assessment this pump does not lies under the umbrella of API-610. In the same way, allowable load of API-610 are not applicable for your case. Moreover, use of API 610 module of CAESAR II is not applicable here.
The suction nozzle seems to be connected with a vessel, not a pump. So use WRC calculations or some good engineering practice(Rosschim-Markle) to get allowable loads for suction nozzle. Similarly calculate vertical distance form suction nozzle to pedestal/leg in order to calculate the thermal displacement required for analysis.

In the same way, for discharge nozzle, you may use the same approach. But you should get a detailed drawing of pump (especially around discharge nozzle) and then to decide.

Regards,
Ali Raza Bashir
Piping Stress Engineer

Getting allowable loads from the manufacturer is compulsory.

I strongly recommend against treating it as simply a pressure vessel.

This is a canned pump ... clearly not API 610 where the allowable loads aim to limit shaft deflection and pump body / casing distortion.

I agree with Michael, get vendor allowables, and if not available think about pressure vessel load limitation, possibly from NORSOK.

It seems that thermal loads are available on the vessel and on the pump. So I would suggest you to model both vessel and the pump for the thermal loads to be able to get adequate nozzle loads that you are after.

Is it really an API pump? As suggested the nozzle loads should be asked the vendor. In case the pump is based on an EN standard the standard may give you the allowable nozzle loading, or refer another one.

According to the technical sheet provided by the vendor, the applicable stanbdard is ISO 13709:2009 (API Std 610 11th Edition).
In this case, could you please answer the 3 questions I asked on top ?

Thank you

Regards,

N.Bongo
Pipping and mechanical equipement engineering.
Tractebel ENGIE
Paris, FRANCE

Image: http://www.hostingpics.net/viewer.php?id=611631PompeHPfostonkin.png

Looking at API 610 11th Edition, section 4.2.2 Pump Designations and Descriptions, your pump fits none of the models defined but is in some ways similar to a VS7 shown in Fig. 18.

If you want to avoid obtaining allowable loads from the vendor you might consider this:

Answering your questions above …. my opinion since you are not really complying with API610

1. Top nozzle is your discharge nozzle.
Side nozzle is the suction nozzle.

2. Loads on neither nozzle will have any real influence on pump performance. Therefore your closest model is a vertical in-line pump since the vectors from pump nozzle to centre-line / support are not relevant in terms of potential shaft misalignment.

3. Ref. point 2, the base plate location is not relevant to loads, but might possibly be important in a pipe stress model for expansion.