5 troubleshooting strategies for optimizing oversized pumping systems
TRANSCRIPT
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MAY 2015 Vol. XXI, No. 5www.FlowControlNetwork.com
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TECHNOLOGY REPORTVALVES & ACTUATORS
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There are several potential ways to
address an oversized pump and system
condition, including the following:
1. Install a different pump.
2. Modify the control strategy to in-
clude a flow recirculation line.
3. Trim the impeller.
4. Install a variable frequency drive
(VFD).
5. Reduce pump speed.
1
Install a Different PumpInstalling a different pump will typically
be the most expensive option and may
only be feasible if considerable energy
savings or reliability savings are avail-
able from the current installed condi-
tion. Many pump upgrades will require a
new baseplate and piping modifications
on the suction and discharge. Given
this fact in tandem with the upfront
cost of the pump itself, this would likely
be a last resort if none of the other
possible solutions presented hereafterare deemed to be viable. If a different
pump is chosen, then other reliability
improvements should also be evaluated
with the pump setup, such as fixing
any piping issues, baseplate issues, or
pump upgrades that may not have been
available when the original pump was
installed.
2 Add a FlowRecirculation Line
Adding a flow recirculation line on the
14 | May 2015 Flow Control Magazine
OPTIMIZING
OVERSIZEDPUMPING SYSTEMS What to do when your pump is too big for your system
By Randy Riddell, CMRP
Figure 1. Impeller reduction and recirculation line operating points
Various studies have shown that many process pumps
are oversized. Optimizing oversized pumping systems
can save large amounts of energy, as well as make an
impact on pump reliability by reducing pump vibration and
extending bearing, seal and impeller life. Oversized pumps
will operate to the left of the best efficiency point (BEP) on
the pump curve, creating significant internal recirculation,
low-flow cavitation, and high shaft loads.
C O U R T E S Y
S C A
YSTEM DESIGN | Pumping Systems
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pump will improve the pump efficiency
as the pump operation moves to the
right on the curve, but the total energy
consumption will increase with a flow
bypass control strategy. This can be a
viable option if the pump is small with
low-flow conditions without significantconsequences for wasted energy. The
new operating point for adding a flow
recirculation line can be seen in Figure 1.
3 Trim ImpellerOne of the most common actions for an
oversized pump is to trim the impeller.
Trimming an impeller reduces energy
consumption due to excessive head
from an oversized pump; however it
does little for over capacity of the pump
sizing, as shown in Figure 1. Trimmingan impeller can, in some cases, lead to
lower pump efficiency.
While trimming the impeller has
drastic effects on the pump, determin-
ing how much to trim the impeller is typ-
ically dictated by the system and/or con-
trol valve operation. The impeller should
be trimmed to get the control valve in
the system to operate in a reliable posi-
tion, which is typically 40 to
60 percent open. If the con-
trol valve differential pressure(ΔP) is in a more closed posi-
tion (e.g., 25 percent open),
then the impeller should be
trimmed to obtain a more
reliable control valve position
(55 percent open). The pres-
sure drop can be estimated
by the control valve equation
by getting the Cv for each
valve position.
Figure 1 shows a pump
operating at 1,000 GPM at65 ft. with a control valve
typically running 25 per-
cent open. The calculated
pressure drop difference to get the
control valve at 60 percent open was
15 ft. The impeller was trimmed from
~13.25x12.5” to ~12.25x10.62” di-
ameter to accomplish a 15 ft. head re-
duction.
4 Install Variable
Frequency DriveVariable frequency drive (VFD) applica-
tions on pump systems can be a good
solution to remove wasted energy by
removing a control valve. By removing
waste head from the control valve pres-
sure drop, the pump can slow down.
This reduces the pump brake horse-
power (BHP) needed due to the lower
head requirement.
Most of the time when a VFD is in-
stalled, the original motor is left in place
and motor efficiency losses are small
and neglected. During a conversion to
a VFD, the original motor may go from
90 percent loaded with 0.87 power fac-tor and 94.5 percent efficiency to 50
percent loaded with energy reduction,
which may lower the motor power factor
to 0.6 and lower the efficiency to 93
percent. On the other hand, the pump
efficiency could increase 5 to 10 per-
cent, depending on the orig-
inal operating point.
VFDs are only viable forhigh-friction head systems,
not high-static head sys-
tems. A VFD is typically only
justified when 50 percent of
the total head is due to dy-
namic head in the system.
VFDs are also not gener-
ally feasible if the process
system feeds a lot of differ-
ent control valve systems.
In these types of systems,
header pressure control isrequired for the VFD con-
trol to meet all of the sys-
tem pressures required to
manage all feed sources. This typically
results in a fairly high system pressure,
just slightly lower than the fixed-speed
design, as the highest pressure source
becomes the driving factor in the pres-
sure setpoint. With multiple sources, it
is important to carefully evaluate each
control valve operation in the system.
As such, it may be difficult to justify aVFD on these type of control systems.
Figure 2. 1200 RPM pump curve original operating point
C O U R T E S
Y
S C A
Reducing pump speed may be thebest option for optimizing an over-
sized pump if the process condi-
tions and pump hydraulics will sup-
port it. Lowering pump speed will
improve the hydraulic cavitation
characteristics of the pump by
lowering net positive suction head
required (NPHSr), improving bear-ing life, and saving energy.
“
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5 Reduce Pump SpeedReducing pump speed may be the best
option for optimizing an oversized pump
if the process conditions and pump
hydraulics will support it. Lowering
pump speed will improve the hydraulic
cavitation characteristics of the pump
by lowering net positive suction head
required (NPHSr), improving bearing
life, and saving energy.
Consider the pump curve in Figure2, which was operating at 1200 RPM. It
originally had a 300-horsepower motor.
Suction energy adjustments to NPSH
resulted in an NRSPr of 28 ft. The net
positive suction head available (NPSHa)
in the system was 15 to 19 ft. Insuf-
ficient NPSH caused pump cavitation,
which elevated typical vibration levels
as high as .4 in/s. The control valves in
the system operated 25 to 35 percent
open, which presented the opportunity
to reduce pump head.
This pump operating at a slower
speed, 900 RPM, shown in Figure 3,
presented a good alternative to the
original oversized condition. Since the
pump was slowing down and couldonly slightly reduce the head, a larger
impeller had to be installed. This pump
would need a 20.75” impeller operating
at 6,000 GPM at 85 ft. Due to shifting
the operating point, the pump efficiency
improved to 78 percent. Due to system
head reduction, this pump would only
require 165 BHP, which also meant a
smaller 200-horsepower motor. This
would be a critical factor, as moving to
a smaller motor horsepower would allow
the 900 RPM frame to fit on the exist-
ing 300-horsepower baseplate, whichmade this an even more attractive so-
lution.
When suction energy and NPSH
margin were calculated, the NPSHr for
this pump at a lower speed was 12
ft. This would drastically reduce the
pump’s cavitation potential. As a result,
vibration was reduced to 0.11 in/s. This
was not a huge surprise as suction en-
ergy is a function of the square of the
speed. The pump system control valves
were now operating in the 50 to 70 per-cent open range.
Not every pump system will work
out where all the factors align to allow
a modification along the line of what is
described above; however, looking at all
options will help produce the best pos-
sible result. No matter what your budget,
there is usually some measure of incre-
mental improvement that can be em-
ployed to improve the efficiency and reli-
ability of an oversized pump system. FC
www.sca.com
YSTEM DESIGN | Pumping Systems
Find related content @ flowcontrolnetwork.com…Search on:FLOWSTREAM
Cavitation | Energy Efficiency | Impeller | NPSH | Pump Curve | Reliability
16 | May 2015 Flow Control Magazine
Randy Riddell ,
CMRP, CLS is the
Reliability Manager
for SCA at the Barton
Mill in Alabama. He
has over 25 years
of industrial experi-
ence with a career
focus on equipment
reliability. Mr. Riddell has a BSME
from Mississippi State University and
is a Certified Maintenance & ReliabilityProfessional from the Society of
Maintenance & Reliability Professionals.
He can be reached at Randy.Riddell@
sca.com or 256 370-8105.
Randy Riddell
Figure 3. Pump curve for same pump operating at 900 RPM C O U R T E S
Y
S C A
No matter what your budget, there is usually
some measure of incremental improvement that
can be employed to improve the efficiency and
reliability of an oversized pump system.“
”