In this example, the cooling water supply line shown below suffers a pressure surge when the turbine driven pump drops offline due to a bearing temperature problem. The elbow at node 45 is observed to jump 6 to 8 inches in the Xdirection when the turbine trip occurs. To eliminate the large field displacements associated with the turbine trip, an alternative support scheme must be designed.

Fluid Properties  250 psi @ 140° F

Flow Velocity  6 fps

Water Bulk Modulus  313000 psi
SOLUTION
The magnitude of the pump supply side pressure wave, which emanates from the pump discharge at node 5, can be estimated from
dp = r c dv
Where:
dp = the pressure rise due to the pump’s instantaneous stopping
r = the fluid density
c = the speed of sound in the fluid
dv = the change in velocity of the fluid
The speed of sound in the fluid can be estimated from:
c = [Ef/(r+ r(Ef/E)(d/t))]0.5
Where:
Ef = the bulk modulus of the fluid (313000 psi)
E = the modulus of elasticity of the pipe (30E6 psi)
d = the pipe mean diameter
t = the pipe wall thickness
r = the fluid density (62.4 lbm/ft3)
ρ + ρ(Ef/E)(d/t) = 62.4 lbm/ft3
[1 + (313000/30E6)(8.62 0.322)/0.322] = 79.1875 lbm/ft3
c = (313000 lbf/in2)(ft3/79.1875 lbm)(32.2 lbm ft/lbf sec2)(144in2/ft2)1/2 = 4281 ft/sec
For a more detailed discussion and evaluation of the speed of sound, see Piping Handbook, Crocker & King, Fifth Edition, McGrawHill pages 3189 through 3191
Apply the previously mentioned equation for the magnitude of the water hammer pressure wave.
dp = r c dv = (62.4 lbm/ft3)(4281 ft/sec)(6.0 ft/sec)
= (62.4 lbm/ft3)(4281 ft/sec)(6.0 ft/sec)(lbf sec2/32.2 lbm ft)(ft2/144 in2)
= 345.6 psi
There are two distinct pressure pulses generated when a flowing fluid is brought to a stop. One pulse originates at the supply side of the pump, and the other pulse originates at the discharge side of the pump. This example only deals with the supply side water hammer effect, but the magnitude and impact of the discharge side water hammer load should likewise be investigated when in a design mode.
The time history waveform for both types of water hammer pulses is shown as follows:
Pod  Discharge pressure
Ps  Source (tank or static) pressure
Pos  Suction pressure (while running)
dp  Pressure fluctuation due to the instantaneous stoppage of flow through the pump
Pv  Liquid vapor pressure at flow temperature
There is an unbalanced load on the piping system due to the time it takes the pressure wave to pass successive elbowelbow pairs. The magnitude of this unbalanced load can be computed from:
F unbalanced = dp x Area
The duration of the load is found from t = L/c, where L is the length of pipe between adjacent elbowelbow pairs. For this example, the elbowelbow pairs most likely to cause the large deflections at node 45 are nodes 4575 and nodes 90110.
The rise time for the unbalanced dynamic loading should be obtained from the pump manufacturer or from testing, and it can be determined from graphs such as those shown above. For this example, a rise time of 5 milliseconds is assumed.
CALCULATIONS
L 4575 = 7 + 4(20) + 4 = 90 ft.
L 90110 = 3(20) + 15 = 75 ft.
Area = P/4di2; di = 8.625(2)(0.322) = 7.981 in.
Area = P/4(7.981)2 = 50.0 in2
F unbalanced = dp x Area = (345.6) (50.0) = 17289 lbf
t duration = L/c
= (90)/(4281) = 21 milliseconds, on leg from 45 to 75
= (75)/(4281) = 17.5 milliseconds, on leg from 90 to 110
t rise = 5.0 milliseconds
Because the piping in this example is ductile low carbon steel, the major design variable is the large displacement. The problem is assumed to be solved when the restraint system is redesigned to limit the large displacements due to water hammer without causing any subsequent thermal problem due to overrestraint.

Generate the DLF spectrum files as shown in the following examples.

Define the spectrum on the Spectrum Definitions tab:

Define the force sets on the Force Sets tab.
Three spectrum load cases are of interest in this example: each spectrum separately and the two of them in combination.
The sustained static load case is now combined with each dynamic load case for code stress checks. For operating restraint loads, the static operating case is combined with each dynamic load case, if necessary.

Set the options on the Control Parameters tab as shown below: