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Babcock & Wilcox 1
Kevin RogersMel Albrecht
Michael VarnerBabcock & WilcoxBarberton, Ohio, U.S.A.
Presented to:ICAC NOx ForumMarch 23-24, 2000Washington D.C., U.S.A.
Numerical Modeling for Design Optimization of SCRApplications
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AbstractBabcock & Wilcox (B&W) has utilized numerical modeling
to simulate fluid and combustion phenomena on commercial
contracts for more than a decade. Verification of model predic-
tions with actual field test results has provided valuable feed-
back for model development and refinement. Achieving a highlevel of agreement between field results and the numerical pre-
dictions provides confidence when applying these models as
design tools. This confidence is demonstrated by years of mod-
eling and design practice experience put to use for new and ret-
rofit low NOx
furnace combustion strategies.
Similar challenges of development and verification exist
when extending numerical modeling to include downstream SCR
processes. Modeling approaches are undergoing continual im-
provement predicting component pressure drop, temperature and
chemical specie distributions, mixing efficiencies, and reactor
performance. Building upon prior boiler experience and suc-
cess, numerical modeling is becoming an increasingly valuable
tool for SCR system design optimization efforts.
IntroductionNumerical modeling is an economically effective design and
analysis tool for the simulation of flow, heat transfer and com-
bustion phenomena surrounding boiler components and auxil-
iary equipment. Furnaces, burners, windboxes, steam drums,
pulverizers, electrostatic precipitators, coal nozzles and piping
are only a few examples of the components and equipment that
have been successfully modeled numerically by B&W.
As the collection of project designs and case studies ex-
panded, and as field test results became more available, the de-
gree of success and confidence grew through application expe-
rience and results validation. This type of experience, along-
side the continuum of computer and software development, has
helped to propel the acceptance of numerical modeling by the
power generation industry.
Selective catalytic reduction (SCR) system design has ech-oed a need for similar experience and results validation. Mod-
eling also becomes an instrument capable of mapping the per-
formance characteristics of discrete components or arrange-
ments. Through optimization of the components performance,
an improvement in the overall system design can be obtained.
Retrofit projects in particular can exhibit a strong need for
accurate modeling of flexible design approaches. They are clas-
sically burdened with process conditions and arrangements that
are less than ideal.
Numerical vs PhysicalPhysical modeling has historically been the dominant tech-
nique that has used reduced scale models employed by the sys-tem suppliers, catalyst manufacturers , and end customers. Cata-
lyst sizing and performance criteria have often been set or in-
fluenced by the expected flow and component profiles deter-
mined through physical flow modeling. When specified param-
eters achieve an acceptable value in the physical model, it is
assumed that the field results will be similar. If the acceptance
criteria are based on physical modeling experience, it then be-
comes important to understand how the results could differ when
utilizing a numerical approach. In the end, both modeling ap-
proaches should lead to comparable conclusions that represent
full-scale field operation.
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Numerical modeling offers some advantages over its physi-
cal model counterparts.
In many cases, numerical modeling can more easily and eco-
nomically predict flue gas temperature distribution and
chemical component distributions. (i.e., flue gas NOx distri-
bution, NH3/NOx ratio distribution and mixing phenomena).
Due to its flexibility, numerical modeling permits the study
of an increased number of geometric arrangements or modi-
fications in a more timely manner than is possible with physi-
cal flow modeling.
Numerical modeling can be done at full scale.
Numerical models can be stored for future use and refer-
enced far more efficient ly than physical counterparts. Ware-
housing a physical model is not required.
The input boundary conditions of temperature, flow and com-
ponent concentration profiles can be specified to a higher
level of detail.
Capital investment of model instrumentation and its mainte-
nance/calibration costs are not an issue.
Input conditions can be varied easily to assess system sensitivity.
The data is inherently in an electronic format.
Independent of the modeling approach, the actual inlet con-
ditions and the range of flow/temperature/component mal-dis-
tribution expected should be measured and described as accu-
rately as possible. With downstream predictions influenced by
the upstream inputs, it is sometimes beneficial to move the up-
stream model boundaries to locations where the inlet conditions
are better known or documented.
Validation and Acceptance CriteriaAs modeling efforts on specific projects or case studies ac-
cumulate, a wealth of information begins to build. The result is
a history and case study library that improves verification, as
well as comparative and predictive capabilities.
The variety of SCR system designs and arrangements mod-
eled to date by B&W has aided in the building of such a refer-ence library. To the extent possible and practical, these model
studies are being augmented with field site data and compara-
tive physical modeling results.
Full-scope modeling experience appears increasingly impor-
tant. With the entire process from the boiler through the SCR
modeled, one can develop a more keen understanding of the
direct and peripheral consequences of design changes from the
NOx
generation point to the stack. The ability to manipulate
the design and uncover ways to improve performance with
modifications to the burners, economizers, economizer by-
pass arrangements, flue arrangements, flue internals, reac-
tor design, and even downstream flue gas cleaning equip-
ment, is significantly improved.
The computer models lend themselves to these library-build-
ing efforts, as they are completely and inherently storable in an
electronic data format. Without significant hardship, base models
can be reconfigured to analyze process results from field testing.
It is important that field site measurements be planned to
provide feedback for model refinement and validation work.
However, a high level of comparability to field measurements
is not always paramount. When performing gross level design
optimizations, the use of a model to gauge the relative effec-
tiveness of changes and optional arrangements is often a pri-
mary goal that can be satisfied at reduced accuracy.
With the longer history of use, physical models have achieved
a certain level of acceptability in providing predictions. For this
reason, some numerical validation studies are performed by compar-
ing the results of the numerical approach to those of the physical.
Ideally, each approach should be compared to actual field
results so that each are compared to the real system, not to each
other. Field data taken should be directly compared to model
results. While field data provides the highest level of valida-
tion, it can also become quite costly and requires forethoughton where to place test ports and measurement instrumentation
on the field units. The task of actually collecting the data is
time-consuming and sometimes difficult.
Aside from validation issues, there is typically some given
set of acceptance criteria. These criteria define the target val-
ues which, if achieved, will provide a high level of performance
confidence.
Velocity ProfileThe velocity distribution profile is often reported as a coef-
ficient of variation (Cv) by the following equation:
Cv = 100 /x
where,
Cv = Coefficient of variation expressed as a percent of the
standard deviation about the mean.
= standard deviation
x = mean
Depending on performance requirements, the velocity dis-
tribution requirements at the catalyst inlet can typically range
from 10% to 20% standard deviation from the mean.
The velocity profile through the plane of ammonia injection
can be equally or more important. For a constant ammonia in-
jection flux, variat ions in flue gas velocity through each injec-
tion zone will induce downstream NH3/NOx molar ratio mal-distributions.
TemperatureThe criteria for temperature distribution are typically ex-
pressed as the minimum and maximum deviation about the mean,
rather than as a standard deviation about the mean. The typical
allowable values will range from 20F to 50F.
The average gas temperature can influence the allowable
minimum or maximum. For example, the minimum recom-
mended catalyst operating or ammonia injection temperature
will usually set the allowable minimum. If the average is high,
the allowable deviation on the minus side is greater.
Ammonia to NOx Molar Ratio (NH3/NOx)The numerical approach can easily utilize an inputted inlet
boundary of a field-measured NOx
profile and determine the
NH3/NO
xratio based on predicted dispersion and/or mixing of
injected NH3
downstream.
The criterion for molar ratio at the SCR catalyst face is typi-
cally expressed as a coefficient of variation similar to that for
velocity profiles. The target values can typically range from 5%
to 15% standard deviation from the mean.
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Pressure DropPressure drop was once the primary criterion for many sys-
tem designs. Obscured somewhat by the velocity, temperature
and component profile requirements, it is nonetheless extremely
important.
On retrofit projects, the allowable pressure drop is usually
based on fan or furnace pressure limitations, and the system
operating power-consumption goals. The pressure drop associ-
ated with the catalyst, and at times that associated with a rather
contorted flue arrangement, will rob from pressure drop allow-
able towards the goals of ammonia injection and static mixing.
Comparisons to Physical ModelingComparisons between physical and numerical models have
typically shown an acceptable level of agreement with pressure
drop criteria. An example is a comparison of a physical study
where scaling relationships were used to arrive at full-scale re-
sults from those measured at the model size. Two numerical
models were developed for the comparisons. One was based on
the physical models 1/10th scale, while the other was done in full
scale. Figure 1 provides a view of the arrangement. Pressure com-
parison cases P1 through P3 represent comparable measurement
points between the physical model and that of the numerical. The
comparisons are presented in Tables 1 and 2 below.
The agreement between the predicted pressure drop in the
numerical model and the measured pressure drop in the physi-
cal flow model suggests an adjustment in acceptance criteria
between the two methods is not needed. Each method can be
reasonably assured of providing similar results.
Many numerically-based velocity and temperature profile
results appear to give values that are more on the conservative
side compared to those based on the physical model. Table 3
and Table 4 provide examples. Table 3 represents a particular
arrangement where mixing devices and vane arrangements are
varied from cases V-1 through V-4. Velocity simil itude was not
maintained from the physical to numercal models; however, for
each case, the coefficients of variation for the physical and nu-
merical models were very close in magnitude. The effect of ve-
locity and Reynolds number appear to be more important when
considering dispersion and mixing phenomena as compared to
that of simple turbulent flow pressure drop determination. They
type and order of the rurbulence model used in numerical models
also influences the degree of potential conservatism in the results.
In Table 4 below, cases T-1 through T-3 represent predic-
tions at the catalyst for a constant overall arrangement where
changes in flue internals were made to examining alternate
methods of economizer bypass gas introduction. In this case
the conservatism of the numerical model was significant when
compared to predictions obtained from a physical approach.
Table 1
Physical Model Prediction and Full-Scale Numerical Model Prediction
Pressure Drop Comparison Cases P-1 P-2 P-3Numerical Full-Scale Model Prediction, inches H
2O 0.48 0.18 1.8
Physical Model Full-Scale Prediction, inches H2O 0.50 0.19 1.9
Table 2
Physical Model Measured and 1/10th
Scale Numerical Model Prediction
Pressure Drop Comparison Cases P-1 P-2 P-3Numerical 1/10th Scale Model Prediction, inches H
2O 0.45 0.16 0.54
Physical Model Measurement, inches H2O 0.46 0.17 0.55
Table 3
Physical to Numerical Velocity Profile Comparisons
Velocity Profile Comparison Cases V-1 V-2 V-3 V-4Relative Numerical Model to Field Gas Velocity 1.0 1.0 1.0 1.0Numerical Model Velocity Coefficient of Variation, % rms 17 20 19 22Relative Physical Model to Field Gas Velocity 0.6 0.6 0.6 0.2Physical Model Velocity Coefficient of Variation, % rms 15 17 18 17
Table 4
Physical to Numerical Temperature Extreme Comparisons
Temperature Extreme Comparison Cases T-1 T-2 T-3Relative Numerical Model to Field Gas Velocity 1.0 1.0 1.0Numerical Model Temperature, max & min +/- of the average +59/-49 +148/-80 +56/-62Relative Physical Model to Field Gas Velocity 0.6 0.6 0.6Physical Model Temperature, max & min +/- of the average +10/-28 +60/-36 +32/-34
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System Design OptimizationWith the high performance duty of many contemporary SCR
designs, optimization techniques are of ever-increasing impor-
tance. Numerical modeling has been demonstrating itself as a
very useful tool, not only for the design of a specific project,
but also for product design development and generation of in-
formation to improve optimization methods.
In the past, much less importance was placed on tempera-
ture and chemical component distributions. Flue systems were
designed with splitters and/or vanes to achieve the simple goal
of minimizing pressure drop. Today, the optimization exercise
can become rather convoluted as attempts are made to improve
temperature and component distributions in ways that minimize
degradation of velocity profiles and system pressure loss charac-
teristics.
Achieving uniform distribution profiles at the SCR catalyst
face with regard to NOx concentration, NH3/NOx molar ratio,
velocity and temperature is often complicated by physical space
limitations, arrangement limitations and limits to boiler modi-
fications. In difficult retrofit applications, a unit length of flue
is a precious commodity for the system designer who is focused
on performance goals. The higher the degree of uniformity re-
quired, the more impractical it is to leave a length of flue de-signed for the lowest pressure drop.
Synergy between these mixing and flow distribution tasks is
critical in restricted space system design, especially when com-
plicated by the need for bypass gas introduction to satisfy mini-
mum allowable temperature requirements. For large side-to-side
or top-to-bottom imbalance, the task of minimizing flue length
becomes quite challenging. While this challenge is being tack-
led with both physical and numerical modeling, it is the nu-
merical approaches that appear equipped with the needed flex-
ibility to address the issues in the time required.
Control ModelsSpecially designed models can be developed to substitute
components from the various modeled systems. In this way,
performance estimates of discrete components or sections on a
side-by-side controlled basis can be made. These control mod-
els can be used to map the performance characteristics of the
devices and arrangements, providing tools to manipulate designs
and focus more quickly on an optimized design. These control
models also allow shortcomings of the particular program soft-
ware or model design approach to become more apparent and
identifiable.
An example of using numerical modeling to characterize
components in ways that facilitate system design optimization
is in the area of blend functions. In this case, a dimensionless
blend number can be used to describe the degree of blendingachieved. This blend number Bn
can be described as follows:
Bn = 1 - 1/0
where 0 is the standard deviation of the component at the inlet
of the dispersion or mix zone and 1 is the standard deviation
of the component at the outlet of the dispersion or mix zone.
As the standard deviation at the outlet of the zone (1) drops
with respect to the inlet standard deviation (0), the blend num-
ber will asymptotically approach a value of 1. Therefore, the
higher the blend number, the greater the degree of blend.
However, a high blend number does not necessarily indicate
a high blend or mixing efficiency. It may have been achieved
by very long lengths or by high energy consumption. There are
three primary degrees of freedom. One is the process result,
such as the degree of homogeneity required. The others are
length and energy. As the length variable drops, the energy re-
quirement increases and vice-versa. If you find you are not
achieving the process result within the allowable length and
pressure drop, then a higher efficiency system must be sought
or the required process result must be lowered.
Both the spatial and energy efficiencies of devices and ar-
rangements can be assessed to provide insight into the optimi-
zation exercise. Spatial efficiencies provide an indication of the
degree of blend achievable per unit length or volume. Energy
efficiency values provide an indication of the degree of blend
per unit energy dissipation rate. A bend, an expansion or con-
traction, and even a straight length of flue can perform a static
mixing function. Alone, their efficiency is often low in terms of
achieving a blending process result. However, when augmented
with internals designed to capitalize on the arrangement and
the flow profiles throughout, their efficiency with regard to
blending can be enhanced. Test programs utilizing numerical
modeling as an analytical tool can be performed to map these
characteristics.
Optimization ExercisesModel construction and run time are major considerations.
Higher order turbulence models require both greater capital in-
vestments in software and computing power, as well as the time
requirements to construct the model and run cases to conver-
gence. With an increasing demand for fast project execution,
the project schedule can often dictate the allowable model de-
tail and number of iterations. While reductions in program de-
tail can save time, they also tend to generate conservatism in
the results. With simpler numerical models demonstrating them-
selves as compelling tools for assessment of the performancechanges versus configurat ion changes, one has to be very astute
to not over- or under-detail the model structure.
The output can be configured in ways that facilitate post-
processing by either system performance programs or optimi-
zation exercises. For example, the output of the model can be
configured for direct input into reactor performance profiling
programs. In this way, the reactor performance based on the
catalyst activity, volume and inlet profile variations can be predicted
to assess allowable operating and control system response tolerances.
Often a target value for NH3/NOx molar ratio at the catalyst
face is first attempted by adjustment to the ammonia injection
grid design and/or flow profiles through the plane of injection.
Figure 2 provides a hypothetical case of resultant molar ratio
distribution at the catalyst face. In this example the NH3/NOxcoefficient of variation at catalyst face is approximately 17%
when no static mixing or ammonia injection zone flux adjust-
ments are made. For visualization purposes, Figure 2 shows the
concentration to each zone as a simple percent deviation about the
mean for each of forty-two zones across a reactor inlet cross-section.
In this case, the target molar ratio coefficient of variation at
the catalyst face was 7%. Fortunately, the system design could
tolerate some pressure drop expenditure for velocity profile
adjustment upstream of the ammonia injection grid (AIG) and
on a static mixing function downstream of the AIG. After sev-
eral options were modeled, the best distribution achievable
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within the allowable pressure drop was a 9% coefficient of varia-
tion. Figure 3 depicts this distribution as the percent deviationabout the mean.
In both cases, no ammonia injection grid tuning is used; that
is, the ammonia flow to each injection grid zone is identical
and constant. The ammonia concentration profile produced at
the reactor inlet cross-section from individual injection zones
was predicted to facilitate AIG flow tuning. Figure 4 provides
an indication of the coverage a single injection zone has in this
particular arrangement.
Modeling of a case where the flow of ammonia to each in-
jection zone is biased to help account for NOx, and primarily
velocity maldistribution at the ammonia injection plane, gave
confidence that the target value could be achieved with a pre-
dicted 5.3% standard deviation from the mean. Figure 5 depicts
this distribution as the percent deviation about the mean.Models are also valuable in optimizing ammonia injection
zone quantity and geometry. The projected dispersion pattern
at the catalyst face based on variations to ammonia injection
zone design can be analyzed to provide the maximum control-
lability with the minimum zone quantity. Not only does this
knowledge assist in design optimization efforts, but it can give
insight to field start-up crews on the projected responsiveness
of each ammonia zone flow control valve.
SummaryNumerical modeling will be continually influenced by ad-
vancements in programming and computing power. Equally
important, however, is the degree of application-specific expe-
rience, which often proves to be the key to a successful optimi-
zation in a timely fashion.
Verification of model predictions with actual field test re-
sults has and will continue to provide valuable feedback for
model development and refinement. Confidence in the numeri-
cal modeling approach will be increased as further field results
and numerical predictions are obtained and compared. As model
libraries are expanded and comparisons are documented, the
application of numerical models for design optimization will
be similarly improved.
Figure 1 Contours of static pressure on a plane through theSCR system.
0.0
-0.5
-1.0
-1.5
-2.0
Static Pressure (in. H2O)
Figure 2 NH3/NO
xratio without static mixing or injection zone
biasing.
Deviation from Mean, %
Figure 3 NH3/NO
xratio with static mixing and no injection zone
biasing.
Deviation from Mean, %
Figure 4 AIG control profi le.
NH3, ppmdv
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Copyright 2000 by The Babcock & Wilcox Company,All rights reserved .
No part of th is work may be publi shed, translated or reproduced in any form or by any means, or incorporated into any informat ion retrieval system,without the written permission of the copyright holder. Permission requests should be addressed to: Market Communications, The Babcock &Wilcox Company, P.O. Box 351, Barberton, Ohio, U.S.A. 44203-0351.
Disclaimer
Although the information presented in this work is be lieved to be reliable , this work is pub lished with the underst anding that The Babcock & WilcoxCompany and the authors are supplying general information and are not attempting to render or provide engineering or professional services.
Neither The Babcock & Wilcox Company nor any of its employees make any warranty, guarantee, or representat ion, whether expressed or implied,with respect to the accuracy, completeness or usefulness of any information, product, process or apparatus discussed in this work; and neither The
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Figure 5 Mixing plus biasing.
Deviation from Mean, %
In addition to specific project modeling and optimization,
numerical modeling is becoming an increasingly valuable tool
for mapping and characterizing the performance of discrete com-
ponents within the system. As the knowledge of the performance
of discrete components and arrangements grows, so does the
ability to select and choose the most appropriate design path in
the most expeditious manner.
References1. K. Rogers, M. Milobowski, and B. Wooldridge, Perspec-tives on Ammonia Injection and Gaseous Static Mixing in SCR
Retrofit Applications. Presented at EPRI-DOE-EPA Combined
Utility Air Pollutant Control Symposium, Atlanta, Georgia,
August 16-20, 1999.
2. A. Sayre and M. Milobowski, Validation of Numerical
Models of Flow Through SCR Units. Presented at EPRI-DOE-
EPA Combined Utility Air Pollutant Control Symposium, At-
lanta, Georgia, August 16-20, 1999.