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1d performance of axial compressor
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1d performance of axial compressor1维轴流压气机性能分析
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Axial compressor performance modelling
with a quasi-one-dimensional approach
N M White, A Tourlidakis and R L Elder
School of Mechanical Engineering, C ran eld University, Bedfordshire
Abstract: This paper describes a technique for the numerical modellin g of axial comp ressors using the
simplest form of representation—a mean-l ine one-dimensional method. Although this type of ow analysis
is a gross simpli cation of a complex three-dimen sional system, which can now be mo delled more accurately
by many of today’s compu tational uid dynamics (CFD) packages, it does offer th e advantages of simple
inpu t requirements and fast convergence times. These factors were major considerations when choosing a
predictio n method to be employed within an optimization program developed at Cran eld for the
optimi zation of stator vane stagger angles, where detailed stage data were not required. The objective was
to develop a technique capable of simply modelling the ow in multistage compressors to provide
performance data including overall pressure ratio , ef ciency and ow range at various speeds, as well as
providing interblade data so that restag gering of blades could be accounted for. The salient issues presented
here deal rstly with the construction of the compressor mo del and its incorporation into a FORTRAN
program. A discussion of the results then follows, where fo ur very different compressors have been
modelled . Finally, the stability limit (or surge point) prediction methods are reviewed.
Results have shown that consistent agreement can be obtained with such a performance prediction model,
providing the loss and deviation correlations used are applicable to the b lade pro les. It was also apparent
that the two simplistic methods of surge prediction, which relied upon either stage or overall characteristic
gradien ts, gave better agreement than the more rigorous discrete stage-to-stage model. This was thought to
be a result of the continuous nature of the empirical rules utilized, which predict a smooth stage characteristic
and hence falsely delay the estimated instability point.
Keywords: axial compressor, peformance prediction, empirical mod els
NOTATION
A
(
x
) cross-sectional area
c
blade cho rd
c
ax
axial chord
C matrix of steady ow parame ters
C
f
coef cient of friction
C
p
speci c heat at constant pressure
C
v
speci c heat at constant volume
D
eq
blade equ ivalent diffusion ratio
D
F
blade diffusion factor
E
net
net stage work inp ut
F
net
net stage force
F
xs
axial blade force de cit (dissipation)
F
xt
axial blade force de cit (lift)
G
ratio of speci c heats
h
blade hei ght
H
boun dary layer form factor
D
H
stage total enthalpy rise
H
* boun dary layer heads shape factor
i
inciden ce angle
K
B
blocka ge factor
m
,
m
1
deviation correlation constants
M
Mach number
N
compressor rotational speed (r/min )
NSTA number of stages
o
throat width
P
total pressure
P
r
total pressure ratio
P
s
static pressure
R
blade radius
Re
Reynol ds numb er
s
blade-to-blad e spacing
t
blade maximum thickness
T
total temperature
T
s
static temperature
U
rotor speed
The MS was received on 7 September 2001 and was accepted after revision
for publication on 18 December 2001
181
A06101 # IMechE 2002 Proc Instn Mech Engrs Vol 216 Part A: J Power and Energy
V
total velocity or stage volume
V
a
axial velocity
V
w
whirl velocity
W
mass owrate (kg/s)
W
sg
surge mass owrate (kg/s)
X
dyn
vector of dynamic perturbations of ow
variables
Z matrix of geometric parameters
a
air angle (deg)
b
blade ang le
g
stagger ang le
d
deviation angle
d
¤
boun dary layer displacement thic kness
e
blade tip clearance
Z
isentropic ef cie ncy
y
blade cambe r angle
y
¤
boun dary layer momentum thickness
n
Prandtl–Meyer expansion angle
r
density
s
solidity
c
/
s
o
loss coef cient
Subscripts
ch choke cond ition
corr corrected
cr critical sonic co ndition
d design condition
ew endwall loss
h hub
in stage inlet station
m mean
ml minimum loss condition
opt at optimu m condition
out stage outlet station
p pro le loss
s shock loss
st at stall condition
t tip
te trailing edge station
tot total loss
0 stagnation condition for normal shock
1 blade inl et station
2 blade ou tlet station
1 INTRODUCTION
The ability to pred ict the overall performance of modern
day, multitstage axial ow compressors with a good degree
of con dence is a paramount require ment for the designer.
To date, there have been many different approac hes to this
problem, all of which can be categorized into the following
three methods: one-dimensional mean-line methods, two-
dimensio nal through ow methods and three-dimensional
computa tional uid dynamics (CFD) methods. In most
cases, however, the approach has been to mix some elements
of the above methods, creating quasi-one-dimensional, two-
dimensio nal and three dimensional models. The term ‘quasi’
is used in this paper to indicate that some three-dimensional
effects are included within the correla tion set utilized within
the one-dimensional approach.
References [1] to [7] presen t a selection of quasi-one-
dimensio nal methods from the literature, spanning over 2 0
years and each employing a different procedure to quan tify
the aerodynamic conditions across a stage. In most cases,
results have shown that agreement to within a 5 per cent
margin for
W
,
P
r
and
Z
of the test data was possible for a
variety of different compressors. In order to account for the
three-dimensio nal ow effects within each stage and yet still
assume an essentially one-dimen sional ow regime, a highly
empirical ap proach is generally necessary. For this reason,
the success of the prediction is heavily reliant upon the
quality of each correlation u sed within the model. The input
data requiremen t does vary for different methods but can be
regarded as minimal when compared with the other more
complex strategies. Howell and Calvert’s program [1] is
generally regarded as a standard for one-dimensional multi-
stage compressor prediction. It conti nues to be used by
designe rs and researchers of various organizat ions, and
some results from this method are compared with those
presented within this work.
The two-dimen sional approac h is most often termed the
through ow or streamline curvature problem. Here, the ow
is considered in the meridional plane, assuming the ow in
the circumferen tial direction is steady. This type of model is
most often used to design the blade geometry given the
desired pressure and temperature rise, as described by Gonc
and Ucer [8]. A secondary role, however, can be for
performance prediction when given the blad e geometry
and some information about the blade performance. A
number of radial stations from hub to tip will be selected
for analysis at each blade row through the compressor. This
is in direct contrast to the more simple approach of the one-
dimensio nal models where the radial mean height is usually
selected for the position of the single calculation streamline.
Soluti on of the compressible Navier–Stokes eq uations in
Reyno lds averaged form, leading to the turbulence manifest-
ing itself as stress upon the mean ow, can be regarded as
one of the most rigorous methods currently used to predict
the three-dimensional ow eld with in a compressor. Chen
and Lee [9] present work using this type of model where an
unstead y ow eld is solved for a single stage within a
turbine. Obviously, th is type of model is the best equipped
to predict all aspects of the ow, but this does come with the
penalty of a very high computational requirement. For this
reason, a full three-dimensional analysis is usually applied
only in the nal stages of the design process. The quasi-one-
dimensio nal and two-dimensional methods therefo re remain
importan t tools that can supply a more rigorous three-
dimensio nal model with early estimates for the ow
parameters.
Proc Instn Mech Engrs Vol 216 Part A: J Power and Energy A06101 # IMechE 2002
182 N M WHITE, A TOURLIDAKIS AND R L ELDER
The purpose of the present study is to select from the
open literature a set of correlations that collectively give a
good overall performance prediction at design and off-
design conditions for a range of different compressors
with conventio nal blade pro les (pro les with circular or
parabolic camber lines). A quasi-one-dimensional numerical
model will then be developed in the form of a FORTRAN
program. The program will be subsequently coupled to a
surge prediction model also written in FORTRAN and
previously develo ped at Cran eld by Gill and Elder [10]
and Escuret and Elder [11].
It is intended that these two prediction programs will be
nally incorporated (as subroutines) into an optimization
program for geometry settings. This is mentioned in more
detail later on.
2 CORRELATION REVIEW
There are two basic requirements for the prediction of stage
performance of an axial ow compressor [12]. The rst is
knowledg e of the variation in the outlet ow angle as a
function of the inlet ow angle, and the second is knowledge
of the variation in the losses or ef ciency, again as a
function of inlet ow angle. Cetin
et al.
[13] described
work that had been directed towards selecting the most
promising correlations for off-design loss coef cient and
deviation from the literature and improving them to account
for transonic and three-dimensional effects. Miller and
Wasdell [3] and Wright and Miller [4] presented a different
set of correlations that had originated from other sou rces but
subsequ ently improved to account for effects such as
Reyno lds number and compressibility. They were successful
in predicting the off-design performance for a selection of
high-sp eed compressors.
The work described in this p aper required individual
bladerow analysis to ensure that the axia l mismatching
between rotor and stator blades was captured at off-design
condit ions. Moreover, the correlation set had to offer stable
convergence for the whole comp ressor operating range.
Resultin g from these considerations, the moss successful
correlation set suggested in reference [13] was chosen for
comparison with those given in references [3] and [4]. In
each case, the actual method is similar and can be summar-
ized as follows: rstly, a blade loading parameter is found
such as the equivalent diffusion ratio
D
eq
at the minimum
loss incidence
i
ml
. The velocity and ow angle te rms that
correspon d to th is minimum loss cond ition are estimated by
assuming that
V
a
remains constant at inlet and exit to the
bladerow and
a
1 ml
and
a
2 ml
are given by the correlations for
i
ml
and
d
ml
. The corresponding pro le loss parameter,
o
p ml
, is then estimated for the minimum loss incidence
condit ion using a co rrelation based upon the classic Lieblein
approach [14]. Secondly, the shock loss
o
s
is found for high
inlet Mach numbers, estimated from a simple, normal shock
analysis. Finally, the combined magnitude of
o
pml
and
o
s
is
corrected for the actual incidence, using a suitable function
that approximates the blade loss c haracteristic. The deviation
is also corrected for the actual incidence. The effects of
endwall lo ss
o
ew
and blockage
K
B
are subseque ntly
introdu ced to give the total loss coef cient
o
tot
.
2.1 Selected correlations
Table 1 lists the origin of each set of correlations u sed
within this study. The suggested method for estimating
o
p
in reference [13] was the Koch and Smith technique,
presented in detail in reference [15]. The in uences of
streamtube contraction, Rey nolds number, Mach n umber
and blade surface roughness upon the loss were included to
produce an effective model that was found to give agree-
ment with test results for compressors with a wide range of
design parameters. The correlations used to account for off-
design incidence and deviation in set 1 were those of
Creveling [16]. This choice was also based upon the ndings
given in reference [13], where it was shown th at the equation
set gave the best agreemen t with the available test data.
The shock loss coef cient,
o
s
, was estimated from two
different models, one for each set. In set 1, the techniqu e
was again that suggested in reference [13], where the
subson ic but su percritical loss was found with the Jansen
and Moffatt method [17] and the supersonic loss was found
with the Swan method [18]. The second model, used in set 2,
was that of Schwenk
et al.
[19] applied in the same way as
given in reference [4]. This particu lar loss component is a
dif cult mechanism to approximate well, in particular the
interaction of the passage shock wave and the suction
surface boundary layer is a major factor that should be
consid ered. As sonic conditions are approached, the ow
becomes very sensitive to c hanges in ow area and a blade-
to-blade description may not be very suitable. Bearing these
facts in mind, the loss model employed within a simple one-
dimensio nal mean-line code such as this is likely to be, at
best, a fair approximation of the magnitude and general
trend of such a complex system. Figure 1, taken from
reference [19], shows a simple representation of the passage
shock mechanism. The position of the bow wave intersec-
tion point with the suction surface is determined, and the
suction surface Mach number is then estimated at that point
using the Prandt–Meyer expansion angle
n
. The total
pressure loss across the normal shock wave at this point,
P
01
¡P
02
, is then found from the average of the upstream
and suction surface Mach numbers.
The methods given in references [18] and [19] are quite
similar, and both follow the above procedure for supersonic
inlet Mach numbers. Subson ic inlet conditions that have
exceeded a critical level and caused a supersonic patch on
the suction surface result in a weaker shock wave, and this is
estimated in reference [17] by a simple law that increases
o
p
as
M
1
increases. Alte rnatively, for set 2, the Schwenk
et al.
method is applied for
M
1
ˆ
1:0 and a linear relationship is
assumed between this loss value and that for the critical
subson ic
M
1 cr
where the loss is taken to be zero. The actual
A06101 # IMechE 2002 Proc Instn Mech Engrs Vol 216 Part A: J Power and Energy
AXIAL COMPRESSOR PERFORMANCE MODELLING WITH A QUASI-ONE-DIMENSIONAL APPROACH 183
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