I AM CURENTLY HAVING A PROBLEM WITH AN OVERLOADED
NOZZLE ON A GLASS LINED REACTOR.

THE NOZZLE IS OVERLOADED BY AROUND 5-10%
OF ITS ALLOWABLES
THE VESSEL IS IN SITU,
AS IS THE PIPEWORK.

I CANNOT ADD REMEDIAL SUPPORTS DUE TO CONGESTION AROUND PIPEWORK/VESSEL.

THE PIPEWORK IS PTFE LINED PIPE (CS)
AND CONNECTS TO THE NOZZLE VIA A STD VAN STONE (LAP JOINT) FLANGE
I HAVE MODELLED THE SYSTEM ACURATELY USING
THE NOZZLE FUNCTION OF CEASER

MY QUESTION IS THIS.

IF CEASER CALCULATES NOZZLE FORCES USING STIFF
CONNECTIONS SUCH AS WELD NECK/WELD NECK,

THEN IN A SYSTEM USING LAP JOINT FLANGES,
THE FORCES MUST BE SOMEWHAT LOWER DUE TO SLIPPAGE
AND FLEXING OF GASKETS/BOLTS/BACKING FLANGE

HAS ANYONE ANY INFO ON THIS PHENOMENOM?
IF I CAN REDUCE THE CALCULATED FORCES ON THE NOZZLE,BY SAY 5% DUE TO THE ARRANGEMENT OF LAP JOINT FLANGES, THEN IT WILL SAVE ALOT OF EFFORT
IN RE-CONFIGURING THE SYSTEM.

Nozzles on a glass lined vessel need to be treated as if they are glass - don't be satisfied with just a 5% margin since variation of support installation could result in much more load. Good practice to protect glass lined vessel nozzles is to include a flexible connector like a teflon bellows expansion joint, or a convoluted teflon flex hose with stainless overbraid, in a line to every glass lined nozzle. The flex hose could replace the first spool from the nozzle, if line size is NPS-2 or less. Larger sizes would require inserting teflon bellows expansion joint by shortening a plastic lined spool.