\TEN
A tion of the agree that truthfully numerousNAVAL architect approaches an examina-world of propeller design he is likely to
James Joyce's "world without end" is
"whirled without aimed." There are
paths which exist for the design of
ma-rine propellers, and one is confronted with
difficul-ties in comparing and evaluating these different
paths.
Four design methods have been applied by the
writer to the calculation of propellers for a variable wake single screw Tanker and a twin screw Liner.
The methods applied were those of Burrill,
Eck-hardt and Morgan, Wageningen (according to Van
Manen), and hill, as outlined in the referenced
publications. Each method, while based on thevor-tex theory calculation of lift, thrust and torque,
differs in the initial assumption of the minimum
energy loss condition, and in the correction factors applied for determining the camber and mean line
pitch angle necessary to develop the required lift,
COMPARING FOUR
METHODS
OF MARIIVE PROPELLER DESIGN
THE AUTHOR
prepared this paper while a Society of Naval Architects and Marine
ngi-neering post-graduate student (1957-58) im naval architecture at King's
Col-lege, University of Durham, Newcastle Upon Tyne, England. He is employed
by the Electric Boat Division of General Dynamics Corporation, and is a
graduate of Webb Institute.
INTRODUCTION
thrust and torque. Burrill uses the Gutsche datá
for corrections, Eckhardt and Morgan use theLud-wig-Ginzel camber corrections and Lerbs lifting surface corrections, Van Manen uses the
Ludwig-Ginzel camber correction, and Hill uses empirically derived correction factors.
The object of this paper has been to compare the
four design methods considered, by applicatin to
the de.gn of propellers for two widely differing
ships. It is a hydrodynamic study, and all designs
have been based on thrust identity. No detailed
strength calculations have been made for the pro-pellers. Curves are presented sho;ing the angles of resultant velocity distribution, lift distribution,
camber ratio, incidence angle, pitch, ratio, and effective pitch ratio. In addition the approximate pressure distributions have been calculated at two of the outer blade sections for each propeller, and the results plotted. Typical pressure distribution
calculations are given in the Appendix.
NOMENCLATTTaE r. = axial inflow factor at propeller a' = rotational inflow factor at propeller B(mid) = moulded breadth
b = blade section length
(b' =aver age blade width from the tip to any sec-tion in Hill method.)
BAR, blade area ratio c = blade section length
C1, = block coefficient
C = midship section coefficient
C,., = vertical prismatic coefficient CT = thrust coefficient
CT. = thrust coefficient based on ship speed
CT1 = ideal thrust coefficient
C. = power coefficient - ideal powei coefficient
= lift coefficient
C NACA data design lift coefficient
C1 drag coefficient
D = maximum propellei diameter Dr = draft
EHP effective horsepowei
f maximum camber of mean line 2rr
(g gap ratio in Hill method (g=
J' = advance coefficient
= advance coefficient based on ship speed Goldstein function
thrust coefficient based on propeller
revo-lutions
= local thrust coefficient based on propellei
revolutions
KQ torque coefficient based on propeller
revolu-tions
K'Q = local torque coefficient based on propeller
revolutions
slope rorrection to lift angle, between theo-iy and experiment
K, correction to no-lift angle. between theory and experiment
blade section length
LBP = length between perpendiculars
LWL waterline length
n propeller revolutions per minute
'li = ideal propeller efficiency
Th hull efficiency
PfD - pitch ratio, where pitch is measured to the nose-tail line
p/q = pressure coefficient
q.p.c. = quasi-propulsive coefficient
R = maximum propeller radius r = radius at any blade section T = propeller thrust
THP = thrust horsepower t = thrust deduction fraction t' = local thrust deduction fraction V = ship speed in knots
speed of advance
= velocity distribution over an aerofoi.l
sec--
tion at zero angle of attack1iV velocity distribution over an aerofoil
see-V = tion corresponding to the design load dis-tribution of the mean line
Ua
= velocity distribution over an aei-ofoil cor-responding to the additional load distri-bution associated with ancle of attack.
W = resu,lant inflow velocity ahead of blade
section
W' resultant exit velocity behind blade section w = Taylor wake fraction (mean)
w' = local wake fraction
x = nondimensional radius (nR) y = maximum camber of mean line
. y = curvature correction to mean line
Z = number of blades p = mass density of fluid
À = advance coefficient based on speed of
ad-vance
X0 = advance coefficient based on ship speed
= advance angle
ß, 4, = hydrodynamic pitch angle
(4, pitch angle at any radius by the Hill
method.)
= ultimate wake pitch angle
x = change in angle during flow curvature past a blade section
tan y = drag-lift ratio = cavitation number
(o = Folidity in the Burrill method ((1=
= displacement
Zi'
An effort has been made to use the nomenclature
adopted by authors in the list of references. As a
result, in some cases different symbols are used for the same terms. Nomenclature not defined above is
defined in the text of the paper.
DESIGN PARTICULARS
Following are the particulars for each of the pro-peller designs undertaken.
Single Screw Twin Screw
Tanker Liner LBP B (mid.) Dr. C. (LBP) C,', Head above C n V (service) Taylor w (mean) EHP (naked) EHP (service) T 550 TI-IP (scrvice) 1.688V (1w) T C p!2 I- (1.688 V) T KT
/ n \
pl .60 1 675' 98' 37.9, 57,570 tons .801 .990 .920 25' 105 rpni 16 knots .34 .19 9,822 (model data) 13,260 (esti-mated 333,000 lbs. 1.090 .190 740' 97, 32.0' 39.300 tons .574 .766 20 147 rpm 25.75 knots .09 .08 35,600 (model data) 43,700 (esti-mated) 601,000 1hs. (total) .543 (each) .182 (each)DETERMINATION OF WAKE VARIATION
Given the Taylor wake fraction for the twin
screw Liner and single screw Tanker, it wasneces-sary to determine the radial distribution of wake. The Van Lammeren wake distribution was adopt-ed," adjusted and integrated to give the originally assumed wake according to the momentum mean
given by Yamagata,14
¡R
w' (1w') r dr
where
.c (1w) rdr
The wake variations are plotted in figures 1 and 2 for the Liner and the Tanker.
SELECTING THE OPTIMUM DIAMETER
An optimum diameter was selected for the Liner and Tanker, and the four design methods under ex-ainination used the same diameter for each
propel-ler. Eckhardt and Morgan recommend taking 97
percent of the open water optimum for twin screw
"IR Tanker Figure 1 tip "Io 'fc A 5.- 1O S "Liner" Figure 3
ships, and 95 percent of the open water optimum
for single screw ships, as given by the Troost series. This reduction compensates both for scale effect and
the open water testing of the model screws by
Troost. The diameter found by this "experience" reduction was used for the Tanker propeller.
Burrill has developed a method for
systematical-ly determining the optimum diameter for wake
adapted propellers. A wake variation is assumed
for the ship. By placing smaller diameter propellers
in this wake the mean effective wake acting over the disc increases, making possible higher
propul-sive coefficients at diameters below the Troost open water optimum. Thern calculations are made using a
series of K'TJ' and K'QJ' charts ° which, have
been developed for B.A.R..50 and minimum drag.
By calculating several diameters, the optimum
di-ameter may be selected from a curve of didi-ameter
vs. q.p.c.
KT
1t
.P.c.=__XJ.X
-i---where (1t) is assumed constant, reard1ess of the diameter of propeller. Recent self propulsion tesis
of a tanker model by the National Physical Labora-tory have shown higher q.p.c.'s at as low as 90 per-cent of open water optimum diameter, and have also
shown "t" to decrease with decreasing diameter.
Calculations were made to predict the Burrill
optimum diameters for the Liner and Tanker, and
the results arc plotted in figure 3.
A.S.N,E. Journ,,, A.00st 9Ó0 4ì7
1t
1.23 1.011w
Propeller Diameter 23-2" 19-4" Number of Blades 5 4 101.27V .666 .918 nD 101.27V mD .212 .292 THP (service) =EHP (service) 1 10,790 43,250 (total)
--%
q. pc. q .4 438 "IR
/
i
A.S.N.E. Journal. Auçust 19b0
o so li 7o -Figure 3
.,
"-IRI
Burrill Method. se-tan=constant (based on Theodorsen) (10)
Eckhardt & Morgan Method. tanß
(1_w'\l
xrtanr = constant tanß I S 4 «A*T I .«C4t I t «b S S
It is evident that the q.p.c. vs. diimcter curves
plotted show higher q.p.c.'s at somewhat lower than
the open water optimum diarne 1ers derived from
the Troost curves. The curves are relatively flat
over the range calculated, and ii.tdicate that the
diameter may be varied considerably with only a
small decrease in q.p.c. The Liner propeller diame-ter was chosen to be 19'-4" and the Tanker, 23'-2". It is noted that the Tanker propeller diameter cou!d
have been reduced, according to the Burrill
meth-od of selection.
Despite the many conditions aciped for
mini-mum energy loss, it has been shown on severaloc-casions that the resulting propeller efficiencies do
not vary greatly. and that no one nl the above con-ditions is preferred over another from an efficiency standpoint. To quote,2
From the point of view of overall emcicicy, and apw from any consideration of cavitation or flow brcakdow. there appears to be no material advantage to be gameti
from the adoption of a radial variation of pitch, both in a uniform and in a variable wake stream..
The condition of minimum energy loss adopted
predicates the thrust loading distribution for a
pro-peller. This
is evident when one compares the
x.tanß and x.tanß1 curves for the Hill method.
which deliberately reduces the leading near the tipand hub, with those for the other methods (figures
4 and 5). It will be seen that the same difference is reflected in the C1, curves (figures 6 and 7) and
I
(based on Lerbs) (11)
tanf377iI\1w )
WageningenMethod. tanß
fiw'
tane_77 - constant
,7cOflstant
(based on Troost & tanß
1wi
Vari Manen) (4)Hill Method. tanß tanß
- constant _?71 _Consthnt
(based on Betz) (12) tanß1 tanß
CONDITIONS OF MINIMUM ENERGY LOSS
Variable Wake Uniform Wake
CONDITIONS OF MINIMUM ENERGY LOSS
The Betz condition for the optimum efficiency of lightly loaded propellers is initially used by Hill for
both the design of propellers in variable and uni-form wakes. The thrust distribution is then altered
by Hill in order to reduce tip loading, consequently
changing the values of tan ß as determined from
the Betz condition. The Wageningen and Eckhardt
and Morgan methods use the Betz condition for
propellers in a uniform wake; and the Burrill
meth-od where x.-.tanr=constant for the uniform wake is essentially the same as the Betz condition, since
in both conditions the vortex sheets in the ultimate
wake are assumed to move aft in rigid sheets of uniform pitch.
In both the Burrill' and Eckhardt and
Mor-gan 511 methods, in deriving the optimum efficiency
condition for a variable wàke, the local thrust de-duction factor is assumed constant over the disc,
while in the Wageningen method it is assumed that
1t'
(1w's%
1t
\1w J
TA"4f.K t2 D (;) 2I Ttnt.
I - T*n £ X Tut
L_r Cr. Figure 6. Tanker Figure 8. Tanker
- .-5'
Figure 7. Liner t-t
'7-j
4
.5 Pflc.,4 RATrOAc pnrcn RATIO Et'FECTI' PITCI.4
THRTJST, DRAG, AND EFFICIENCY
We have seen that the hydrodynamic pitch angle
(ß) is determined differently by each of the four
methods. All methods, however, employ,
i
4r.x.k
CL--=
-
sinß tan (ß-f3)
to determine the circulation distribution. k" is the
Goldstein correction factor corresponding to ß,
ex-cept by Bun-ill, where k corresponds to the ulti-mate stream pitch angle (e).
In the Eckhardt and Morgan and the Hill
meth-ods, thrust and power are calculated from the ideal thrust and power distributions, assuming values of
CD.
(i t)
(i+ _LJ1)
Eckhardt and Morgan assume CD=.008 for all
sections, regardless of section thickness ratio or
in-cidence angle. Hill, on the other hand, takes C as derived from Gutsche experiments where CI) is de-pendent on thickness ratio and incidence angle. The
minimum value of C=.0075 occurs at zero mci-dence angle and about .05 thickness ratio. Bun-ill.
plots minimum CD values for aerof oil sections as a function of thickness ratio, and finds the minimum
dCT dCT
dxdx
dC1 dCv,clx - dx
Cr.M*tDT **AA,&?. 5ut*rnj.. n.J&*t.J.4GS.._______J / s Figure 10. Tanker &CAMtCDT 4OCÚ.M -- bORtILL w**tN,MtN Figure 11. LinerrtCCT,VE I1CN RATLD
'L
r j r i
A.S.N.E. Journa'. August 960 439
t I
j
j 4 5 br j n
CAtSFP RATIO AT4t4Lt (DEG..)
Figure 9. Liner
ultimately on the effective pitch curves (figures 10
& 11). In calculating x.tanß by the Wageningen
method 97 percent of the RPM is used (scale effect
correction), resulting in higher x tanß values than given by the other methods. Also, in calculating
x.tanß, the Kramer 71i is reduced to correct for the
difference between the pitch of the wake adapted
screw and the comparable B-series screw. Thus, the higher x.tanß values. These corrections applied by Wageningen in the first stages of a propeller design are essentially pitch corrections. (In making the
correction the thrust can no longer be determined
from the C, distribution calculated.) The other
methods make pitch corrections during the later
stages of design, in allotting camber and incidence
angle.
'4
CD=.0082. It would therefore seem that the Eck-hardt arid Morgan constant C0=.008 is rather low and would consequently predict higher propeller efficiencies than the Hill and Burrill methods for propellers with high section thickness ratio. (See the Tanker and Liner propeller efficiencies given in Table I.)
TABLE I
The Burri.11 method assumes minimum profile
drag and KT and KQ are based on curves for
B.A.R.=.50. For higher B.A.R.'s it is to be expected
that the drag would be underestimated and
conse-quently the resulting propeller efficiency would be
too high. In the Liner design considerably higher
B.A.R. ratios were adopted, the Eurrill K'T and K'Q charts therefore predicting high propeller
efficien-cies. The expressions for K'T and K' should
there-fore be calculated for B.A.R.'s considerably higher than .50, rather than using the K'T and K'Q charts.
The expressions for K'T and K'Q are:
K'« (1
a')2 (1+tan2)sin (+r)
cos rK'
x.tan (+r)
2K'Q(tnqtan).tan (4+r)
where a'= 1+tan çf) t
(+r)
The Tanker propeller efficiency by. the Burrill
method is
in good agreement with Hill, where
B.A.R.=.584. For the Liner and Tanker propellers Eckhardt and Morgan predict higher efficiencies where C0=.008 appears low for the higher
thick-ness ratios adopted.
DIVIDING UP CAMBER AND INCIDENCE ANGLE
Burrili Method
If camber is allowed to entirely develop the
re-quired C1, at a given section, according to theory: i
«oTIi= .0 radians
where a,1.11= theoretical no lift angle of camber.
From experimental results, however, for a single
aerofoil,
«oACT=Kan.
where Ks,, is an experimental correction factor
ob-tained from wind tunnel results and is dependent on thickness ratio and the position of maximum
camber.
When an aerofoil is in cascade, as is the case of a propeller blade, there is an effective increase in the
resultant hydrodynamic inflow angle at each sec-tion due to a change in flow around each secsec-tion. This increase in angle may be represented by iag:
Ka0.
where Kac is based on Gutsche's experiments, and
is a function of the hydrodvnamic pitch angle and the cascade geometry. By Burrill's method is
added to the required incidence angle in order to
compensate for cascade effect, and allows the
cam-ber to develop its full experimental lift value, as shown below:
Zir A'. JI...
From cascade experimental data, the required
to-tal no lift angle may be represented by:
i
i
a2,5( =
K, . . C.
where K, is a slope correction to the CL curve in
going from a theoretical aerofoil to an actual single aerofoil, and is a function of thickness ratio. Km is the Gutsche slope correction to the C1. curve when going from an actual single aerofoil to cascade, and
is a function of the hydrodynamic pitch angle and
the cascade geometry.
It follows, therefore, according to Burrill that the
total angle of incidence (ai) is: al «COR. ±-«m«,,lCT
In converting the camber no lift angle into the appropriate camber, Burrill uses:
J.
(Y'
c K, K5,, e
where
is based on the NACA. aerotoi
re-suits T (i.e. for a.S mean line T11.0679 C1).
In using the a=.8 mean line NACA data it must be remembered that C1,, T is based on an angle of in-cidence as well as camber, and therefore the theo-retical camber no lift angle must be reduced
ac-cordingly.
Eck hardt and Morgan Method
For viscous flow the a.8 mean tine is
recoIn-mended where the camber ratio is equal to .0679 C1,. This camber ratio must be multiplied by two curvature corrections (k1, k) which are functions of the expanded area ratio, and are based on
Eck-hardt and Morgan's evaluation of all numerical
re-Propeller Efficiencies for: Tanker Liner
Burrill Method .545 .705
Eckhardt and Morgan Method .575 .682
Hill Method .550 .640
suits available inì propeller literature. Ludwig and
Ginzel's work on the curvature of flow at the half-way point of each section forms the basis for
Eck-hardt and Morgan's camber curvature corrections.
Further, Lerbs' work on the change of curvature of
flow over the chord length is used to make up for the deficiency in pitch which results in applying
only the Ludwig-Ginzel corrections. The addition-al corrections needed to make up for this pitch de-ficiency are put into angle of incidence. These
cor-rections are necessitated by three factors: blade friction, ideal angle of attack of the mean line, and correction from lifting surface effect. The first two
corrections are combined into one angle of attack ,
which for the a=.8 mean line is: a1.15 C7,
degrees. Correction for lifting surface effect arising from the free and bound vortices is based on a sim-plification of Lerbs' rigorous method of calculation.8This lifting surface correction is made to the face pitch ratio, such that the final pitch ratio:
\ P/D
P!D=x tan (ß1+a,) (1-f
PfDP/D thri (ßj+a2).7 where 1+
PfD tan ¡3.7
and =angle of attack from lifting surface effect.5 PID is at the .7 radius.
Wa.genin.gen Metlwd
Van Manen adopts the Karman-Trefftz profiles, which are built up of two circular arcs, and reads directly from cavitation charts for these profiles
(theoretically calculated at shockfree entrance) the
effective camber ratio required for a given
thick-ness ratio and lift coefficient. The effective camber
ratio found is then corrected for curvature of flow
using the Ludwig and Ginzei curvature corrections
(k); and, further, a friction correction is made
where 35 percent of the frictional decrease in circu-lation is put into angle of incidence and 5 percent into a camber ratio correction. The friction correc-tion factor p. is taken as a constant value of .75.(1/L
\ ( i
f.rr.f 1.3+.7i'. I. 1 f..,.
--geom.=
-1 2 k
HILL Method b'.C1
Hill uses an empirical expression 15R(1x)
as the corrective addition to the theoretical lift co-efficient due to the flow around the propeller blade lip from the high pressure area on the blade face to
the low pressure area on the back. The lift
coeffi-cient, as corrected for tip flow, is obtained then by
using the blade section camber theoretically
re-P/D
quired to develop the given lift
coefficient. Hill adopts a1 camber, because at the time of his paper it was thought that this gave a nearly uniform pres-.sure distribution (for shockless entry), and hence
was best from a cavitation standpoint. Theoretically
for a=i camber a lift coefficient of 1.0 requires a
camber ratio
of .05515. Experiments, howevei-, showed that only 74 percent of the theoretical liftis actually obtained, whereas for circular arc cani-ber 80 percent of the theoretical lift is obtained. For'
a=1 camber the remaining 26 percent of CL is put in angle of incidence. With an angle of incidence
CL is increased at the rate of .1097 per degree.
In addition a curvature correction based on ex-periment is found, which is a function of the
num-ber of blades and and contrary
(gsin- -) cos
to earlier experience, according to the Hill method decreases with an increasing number of blades. This
additional CL required due to the curvature
cor-rection is developed by putting half in camber and
half in angle of incidence. The camber ratio
re-quired for the curvature correction is .10 times the curvature correction expressed in terms of
addi-tional CL. Hence circular arc camber is added to the a=1 camber initially calculated. There is some
cori-fusion on this point in the Hill paper. The design example worked by Hill is done in the manner
de-scribed above, and according to test results is found
in excellent agreement with the actual propeller
model performance. On the other hand, in the
"Comparison of Experiment and Theory" given
earlier in the paper, Hill states:
several propellers were designed using a=1 camber
for the theoretical lift and the tip correction and circular arc for the curvature correction. The experimental thrust
and power coefficients for the wide-bladod propellers D and E were considerably below the calcuiatLd values, but thc reverse was true for the narrow bladed propellers F and G.
- . . The results obtained with propellers D and E indicate
that the combination of two different types of camber is
not satisfactory since it cannot be presumed that each type
of camber will oerform the function for w rich it is intended.
- . - In order to substantiate further the indications that the
combination of circular arc and a1 cr1i>cr behaves as
though all the camber were a circular arc, propeiicr i was made. Propeller I was identical with propeiiti D n all i-e-spccts including the camber ratio of each section. except
that all the camber was circular arc. The experimentally
determined thrust and torque coellicients of propellers D and I were identical.
Despite the fact that, according to Hill above experimental data, all the camber acted as if it were circular arc camber, the camber was calculated for the three designs included in this paper, as hull does in his worked example. Later, in ev;iluating camber
in terms of no lift angle, the cambi-r is considered to be all circular arc camber.
COMMENTING ON CAMBER AND INCIDENCE ANGLE
Camber Ratio
Regardless of the various data and different mean
lines adopted by the four methods in determining
the appropriate corrections to camber ând incidence
angle, it is interesting to note that ali but the
Bur-ri11 method require approximately the same camber
ratios at the .7 radius for the Liner and Tanker
designs (see figures 8 and 9). The Burrill method gave lower camber ratios at the .7 radius. Those required for the Burrill designs were based on the theoretical realtionship between camber and lift
coefficient given in Reference (7) for an a=.8 mean
line:
y_ .0679
-CL
c IÇ.Ka,,
where K, and Ka, are experimental correction fac-tors for slope and camber no lift angle.1 Burrill, however, in the Discussion Section of Reference
(1) has pointed out that the theoretical relationship should be taken as .10 (not as .079 as given in
Ref-erence (7) for NACA 6G mean line) when using NACA four-digit type centerline cambers. It is to
be supposed that similar increase should be made for the a=.8 mean line. Because no data was
avail-able, however, the calculations made for the two Bun-ill Designs adopted .0679.
Eckhardt and Morgan reduce camber to zero at
the tip, and Hill's camber approaches zero. Hill also reduces camber near the hub, whereas Bun-ill calls
for continually increasing cambers at the inner
radii. The Wageningen method increases camber at both the inner and outer radii. This increase incam-ber by the Wageningen method at the outer radii shows bad cavitation characteristics
(to be
dis-cussed later).
ANGLE OF INCIDENCE AND PITCH RATIO
The curves of incidence angle (figures 8 and 9) allowed by the Wageningen method show much lower values than obtained by the other methods.
Actually, the Wageningen incidence angles would be higher than indicated, if measured from thesame
norm as used by the other methods. The curves of incidence angles plotted were measured from the
calculated hydrodynamic pitch angle, which it will
be remembered was increased in the first stage of the Wageningen design by reducing the Kramer
. This is evident in the pitch ratio curves for the three designs (figures 10 and 11) where the
Wagen-ingen pitch is in better agreement with those cal-culated by other methods. While the agreement is
better, it will be remembered that the Wageningen incidence angles are purposely kept low, with hope of attaining shockless entry.
The Liner and Tanker designs show good agree-ment on incidence angle between the Bun-ill,
Eck-hardt and Morgan, and Hill methods
at the .7
ra-dius. Attention is called to the comparatively very
high values of incidence angles determined by the
Bun-ill method at the inner radii for the Tanker
and Liner. (This is also reflected in the pitch ratio curves.) The Gutsche cascade correction factors
(Keg and Kgs) determined from limited wind
tun-nel experiments require high incidence angles aT
the inner radii where the data show that cascade
effect plays a major role. Recent work in propeller
design has taken a skeptical view towards the va-lidity of these Gutsche cascade corrections.
EFFECTIVE PITCH RATIO
Effective pitch ratio may be interpreted
as a
measure of the intended thrust loading distribution on a propeller.
effective pitch ratio=x-r.tan (ß+a1±a,) where a1incidence angle measured to thenose tail line and a0=eamber no lift angle. The Eckhardt and
Morgan and Bun-ill methods both employ expres-sions for determining a,. The (A) effecti'ce pitch ratio curves (figures 10 and 11) for the Eckhardt
and Morgan and Burrill methods are based on these
expressions.t The (B) curves and the Wageningen
and the Hill effective pitch ratios have all been
cal-culated on another basis, where camber is
evalu-ated by means of one expression, regardless of the
type of mean line. It is assumed that the lift
con-tribution of camber, CLI 10 -t, and that it may be
converted into camber no lift angle by means of the theoretical relation
a,,.
CLI or a=91.2 -i-. Themean effective pitch ratios haie been calculated
(Table II), where:
Mean Effective Pitch Ratio
r j Eff PfD
TABLE II
If the .7 radius is considered the basis for coni-parison, all four methods show fair agreement on the effective pitch ratios needed for the Liner and Tanker (see figures 10 and 11). The mean effective pitch ratios calculated by the Hill and Eckhardt and
Morgan methods show excellentagreement for each design, whereas the Burrill and Wageningen
effec-tive pitch ratios for the Tanker
are considerablehigher. The Burrill mean effective pitch ratio for * By the Eckhardt and Morgan
method a
.139 CL3 for NACA a=.8 mean line and by the
Bur-nil method tKao.
Mean Effeetive Pitch Ratios for: Tanker Liner
Bun-ill Method (B) .885 1.211
Eckhardt and Morgan Method (B) .825 1.205
Wageningen Method .848 1253
Hill Method .828 1.210
the Liner is in good agreement with that calculated by the Eckhard and Morgan and Hill methods.
When comparing propellers designed by these
several methods it is doubtful whether mean effec-tive pitch ratio is a justifiable basis for comparison.
While the overall agreement may be good on this
basis, the actual lift contribution of camber and in-cidence angle at particular radii may not be as was
intended by the several methods. Effective pitch ratio, or mean effective pitch ratio as a basis for
comparison, would truly be justifiable only for a
se-ries of propellers where the correction factors of
one method had been used in apportioning camber and incidence angle to develop the required thrusts.
CAVITATION
The Eckhardt and Morgan and the Wageningen
methods of propeller design emplpy incipient
cavi-tation charts in selecting the minimum length of blade sections at outer radii for supposed
cavita-tion-free operation.
Eckhardt and Morgan use
NACA section data and Wageningen usesKarman-Trefftz profile data. The blade widths required by the latter to develop the same lift (see figures 1 &
2) are greater at the outer radii than those required from the NACA section incipient cavitation charts. For the twin screw Liner the blade widths given by
the Karman-Trefftz profile data at the outer radii
were exceedingly high; cOnsequently, reduced
widths were arbitrarily adopted. (i.e. at the .70
ra-dius only 91 percent of the chart width was
adopt-ed.) In both methods 80 percent of the cavitation number (if) based on resultant stream velocity is used for entering the charts. The blade outline
se-lected from the NACA data according to Eckhardt
and Morgan has also been assumed for the Burrill
and the Hill designs of the single screw Tanker and the twin screw Liner.
The following table gives the expanded blade
area ratios which resulted from using the incipient
cavitation charts for the Liner and Tanker
propel-1ers, and the expanded areas recommended by the Burrill cavitation chart.'7 The Burrill chart is based
on actual ship data, and for the Liner and Tanker the expanded blade area ratio given by the chart
is that appropriate to the normal merchant ship line.
Expanded Blade Area Ratio
NACA 66 nose Karrnan-Trefftz arid parabolic profile,
circu-tail with lar arc mean Burrill
a .8 mean line, line and shock- cavitation less entry. data.
Liner (4 blades)
....
.780 .843 (adopted) .738Tanker (5 blades) .. .584 .642 .575
It is noted from the above that the Burrill ship
data allows lower blade area ratios; that the
in-cipient cavitation charts for Karman-Trefftz profilesand circular arc mean line require higher blade
area ratios than the NACA section charts require.
Unfortunately, the use of cavitation charts in
se-lecting blade widths does not take account of the
effect of changes in incidence angle on the pressure
distribution. It is desirable, therefore, after having
selected the blade width, face pitch, and camber of the propeller sections, to check the pressure distri-butions at the outer sections. Since each method of design under investigation divides lift between
cam-ber and angle on incidence in different ways,it was
decided to analyze the resulting pressure distribu-tions by an independent line of reasoning. The final geometric carnbers derived by each of the methods were converted to effective cambers and cavitation
was evaluated in terms of the t1eoretical pressure distributions given for NACA sections and mean lines. The remaining lift, not developed by camber, was assumed to be developed by angle of incidence. In developing the corrections to geometric
cam-ber in order to evaluate the theoretically effective
camber the following method is used:
Theoretical effective camber= (geometric
cani-ber) . K K0,= --where K50 is the correction to
the camber no lift angle in going from the experi-mental value of no lift angle to the theorctically required no lift angle for a given C1. value. K is a
slope correction to the line relating C1. and lift
angle to the theoretically require lift angle for a
given C,,. K and K50 are derived from extensive single aerofoil experimentation and are plotted by
Bun-ill in terms of thickness ratio.06
Takeias the curvature orrecüon
to camber in going from the single aerofoil to an actual propeller section working in cascade. In evaluating it is assumed that the induced axial velocities occurbefore and after the propeller disc, and not in way of the disc, and that the entire rotational velocity
is induced between 10 perccnt ahead of a blade sec-tion leading edge and 10 percent behind the secsec-tion
trailing edge,'9 and that the curved flow follows a
circular arc which passes through these two points.
The angle x in the diagrams below therefore
represents the total change in angle during flow
Q 2TTnn. VTfl
r
Velocity iaram -0-o '1ow curvature 443curvature. From the following diagram Io ,/ ,',..s it is evident that, 1 5 ¿ y :1. 5
s1n7-
=--. -i-b. X yi
=- X
e 9.6 1+awhere X=tan'(thnß.
1-2a' tan'(tan/3. (1+a))and a'=
(tan/?-tanf3)tan(/31+r)1+tanß tan(ß1+r)
tan ß
a= -(1 a') -1
tana
444 A.S.N.E Jouriral, Au'ust I96
Table III
The curvature correction to camber is in effect a macroscopic correction. It is a corret'tion Ofli to the maximum camber ratio of a section and is mere-ly a device for allowing one to predict the total
con-tribution of camber to lift. In general, the pressure reduction on the forward portion of the back of a propeller blade would be greater, and on the after portion less, than is predicted by this method of calculation. In addition,
if there is considerable
contraction of the slipstream behind the propeller. the angle will be overestimated by this method. Thus, the value of effective camber would be un-derestimated, resulting in a higher contribution o incidence angle to the lift developed. in any case
the prediction of face cavitation at the leading edge would be a conservative one, while a thus
calculat-ed absence of back cavitation would he subject to
review.
The pressure distributions around two of the
outer radii sections were calculated by the above
method for all of the Liner and Tanker designs, and the plotted pressure distribution curves (figures 12
and 13) checked for total CL. Integration of the
curves showed the total CL'S to be from 2 percent
lower to 5 percent higher than the required C,
values. This error was not considered excessive. and Table III is based on the corrected pressure
distributions. Typical pressure distribution
calcula-tions are given in the appendix. Liner Burrill Design
max-
q (T C, (integrated) . p ¡(TCorrected
-Cr. (required) q x=.875 .124 .157 .99 .80x.75
.160 .214 .98 .77 Eckhardt and Morgan Designx.90
.130 .149 1.04 .83x.70
212 .243 1.05 .83 Wagehingen Design x=.90 .177 .154 1.05 1.10 x=.70 .203 .251 1.04 .78 Hill Designx.90
.096 .149 1.00 .64x.70
.195 .243 1.04 .77 Tanker Bun-ill Design x=.875 .184 .240 1.02 .76 x=.75 .243 .338 1.02 .71 Eckhardt and Morgan Designx.90
.184 .214 .98 .88 x=.70 .306 .383 1.05 .76 Wageningen Design x=.90 .206 .230 1.05 .86 x=.70 295 .410 1.05 .68 Hill Design x=.90 .151 .214 1.01 .69x.70
.300 .383 1.05 .74In entering the NACA incipient cavitation charts.
Eckhardt and Morgan recommend using .8o and
the calculations made on the resulting sections in-dicate a pressure reduction of from .76.r to .88(7.
Using the same blade outline and same type of sec-tion for the Burrill method shows a pressure reduc-tion of .7L7 to .80(T and for the Hill design, which uses a different NACA section and mean line, there
is a pressure reduction of .64-r to .77g. The lower
value, .64g occurs at the .9 radius, where the thrust
loading has been reduced in the Hill method. The
Eckhardt and Morgan, Bun-ill, and Hill designs for
the Liner and Tanker therefore appear cavitation
free (not in way of the leading edge), by a
sub-stantial safety margin. It is supposed that the bladewidths for all the designs could be reduced at the outer radii if a reduction in this margin were ac-cepted. Certainly the Hill designs could have the widths reduced near the .9 radius where the thrust
loading has been reduced.
Figure 12
The Wageningen Liner design, wi h the increasl in camber ratio which the method prescribes at the
outer radii (see figures 8 and 9), is in danger of
cavitation. The calculated pressure reduction at the.90 radius exceeds the available g by lO percent,
The other radii calculated for the Liner and Tanker show pressure reductions of from .68g to .86g.
In several cases there is a marked reduction in pressure near the back of the leading edge, due to the fact that NACA data was used, whereas in an actual shaping of the nose, with a generous nose radius, the pressure reduction would be reduced.
Also, any thin trailing edge sections would be modi-fied. It is probably safe in assuming from the
pres-sure distribution diagrams calculated that there is no danger of back cavitation at the leading edge.
The Wageningen designs, however, at the .90 radius indicate face cavitation at the leading edge, which
is no doubt caused by the adoption of very little
incidence angle (see figures 8 and 9L
A.S.N.E. ,JeurnI. August ,o 445
'4 o .4.1,
=
.
. . t -. . '7-. .. .t
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.+.-,-4....
4-: 'T;-. .. . . . -.a*su...a
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=::::::::::
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-, ., . î ¡'n "1-._u
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er.::;:
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SOME CONCLUDING REMARKS
The four design methods have been applied in
their entirety, beginning with the condition
of minimum energy loss and ending with the selec-tion of appropriate pitch ratio and camber ratio.Because no attempt has been made to establish
agreement between the corresponding steps of eachmethod, there are few joints at which a
quantita-tive comparison may justifiably be made. The value of this paper has been to show the relative effect of the several different paths followed by each method
considered. These effects have been graphically shown and discussed in some detail in the text of this paper. A further study could be made, where
for each propeller a common optimum load distri-bution is calculated and starting with this as a base,
the mean line pitch and camber ratio are selected,
using the different data of the several methods. This study would make possible a quantitative
compari-Figure 13
um...uuuus...u...m....
u. u.UUUUUUu.UuUUUUUU.uSu..RUuuØuu.u.Uuu.ia.uUuUuu..u.uU..u.uu..UU.U...Uu.uuUuuuSuu.um
..u..u...
u. u uu.u .¡!!!!
tu.ju.r4g.iaut
UILJ--=-J.
___ __
a -u.u u u u. uu u u u su u u.uu £'ja.uuu.uuu.u.uu.u.u..uuu.uuuuuuu.uu.uuuuuuu.uuuu..uauuuuuauu.u.u..0
i u .u..am..u..uua.u.uuupiu.u.mu..uu.u.
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1_î_ .um...u.iu....
t:u:: a.
....u.u...su..
.. uu
u.a.0
m
u l.vmu.uuuuuu
UI! !IIU
U Ui
SSL
#UØpIUIIUTh1I.
uau..
a.us.m---j1jILrnw.mrn.s..a.
ji....
;1au. ..u.uuuauiiUU...U.u,I...
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.
uu..uu.uumum.1.m.0
us.
ummu.u.u.u....u.u...u.u...ue....0
son between the mean line pitches and the camber ratios given by each method. It would then remain
for the propeller designer to determine, with the aid of this information and experimental data for
the designed propellers, which method is desirable for a given design.
ACKNOWLEDGMENTS
The author gratefully thanks his tutor and
teacher, Professor L. C. Burrill of King's College, The University of Durham, for the guidance and
instruction given him when making the calculations
required for this paper. He especially thanks Pro-fessor Burrill for the idea of the method used in
making the flow curvature correction in the
cavita-tion calculacavita-tions. The author also thanks Miss
Sa-rah Luchars for her great help
in preparing the manuscript for this paper."The Optimum Diameter of Marine Propellers; A New Design Method." L. C. BurrilL NECI, Nov. 1955, Vol. 72. "Fundamentals of Ship Resistance and Propulsion," Part B, J. D. Van Manen, International Shipbuilding Progress. June and July 1957, Vol. 4.
'The Design of Wake-Adapted Screws and their Be-havior Behind the Ship," J. D. Van Manen and W. P. A. Van Larnnieren, Institution of Engineers and Ship-builders in Scotland, 1955.
"The Design o Ship Screws of Optimum Diameter for
an Unequal Velocity Field," J. D. Van Manen and L. Troost. SNAME, 1952.
"A Propeller Design Method," M. K. Eckhardt and W. B. Morgan, SNAME, 1955.
"The Design of Propellers," J. G. Hill, SNAME, 1949.
"NACA Report No. 824, Summary of Airfoil Data,"
Abbott, Doenhoff, and Stivers, 1945.
"Propeller Pitch Correction Arising from Lifting
Sur-face Effect," H. W. Lerbs, DTMB Report942, 1955.
"The Effect of Radial Pitch Variation on the
Perform-ance of a Marine Propeller," L C. Burrill and C. S.
Yang, INA. 1954. A. Section Particulars; tic = .057 tanß = .200 CL = .2430 CD = .0086 CD= tan r = .0354 CL r = 2.03° = 17.80° r+ß1 = 19.830 tan (r+/31) = .361 tan ¡3 = .321
"Theory of Propellers," Theodorsen, McGraw Hill, 1948.
"Moderately Loaded Propellers with a Finite Number of Blades and an Arbitrary Distribution of Circulation,"
H. W. Lerbs, SNAME, 1952.
"Schraubenpropeller mit Geringsten Energieverlust," A.
Botz, Nachrichten von der Gesellschaft des
Wissen-schaften zu Gdttingen, 1919.
"Resistance, Propulsion and Steeaing of Ships," Van
Lammeren, Troost and Koning, 1948.
"Measurement of Wake," F. Horn, Symposium on Pro-pellers, NEd, 1938.
"Some Effects of Blade Thickness Variation on Model-Screw Performance," T. P. O'Brien, NEd, 1956. "Calculation of Marine Propeller Performance
Char-acteristics," L. C. Burrill, NECI, March 1944, Vol. 60.
"Developments in Propeller Design and Manufacture
for Merchant Ships," L. C. BurriU, 1MB, 1943.
"Effect of Cavitation on the Performance of a Series of 16 in. Model Propellers," R. W. L. Gawn arid L. C. Bur-x-iii, rNA, 1957.
"La Courbure Induite des Ailes Minces," R. Guil.lotor, Association Technique Maritime et Aéronautique, 1955.
APPENDIX
Typical Pressure Distribution Calculation
SINGLE SCREW TANKER, .7 radius; Eckhardt and Morgan Design
(tan /3-tan /3) tan (r+/3)_0392
a'= 1+tan /3v tan (r+ß1)
tan /3
a =tan/3 .(1-a')-1=1.543
1+a \
= fl1(tan/3
1-2a')
tari-' [tan /3.(1+a)]=.0241 rads.c 9.6 Geometric camber,
.1
= .0270 C K, = .946 (Ref. 16) K00 = .890 (Ref. 16) = .0227 = .0025 C y Effective camber, - = .0202 cA.S.N.E. journal, Auut l96 447
B. Pressure Distribution (Ref. 7): Section: NACA 66-006, a=.8 mean line
CLI=1.00, (y/e) =0679, (tIc) =06, ,=1.54°
x
(4
()
(-.)
For Section under consideration:
t/c
r
(1)=[()
-]
(tic),+1=L()
_1]
(.950)-t-1 zv ¿v ylc(2)=(V)
.(YIC)(V)
.(.298) VaV\
[ =()
.rv
.V LV(4)-1-I
---qLVVV
x .025 .05 .10 .30 (1)-i- 1.033 1.040 1.050 1.064 (2) .083 .083 .083 .083 -.053 -.038 -.026 - .013 Back:rv
v +--
+ --
1.063 1.085 1.107 1.134 Face: rv - v .v«1-v-- -y-j
1.003 .995 .993 .994 (4) Back -.130 -.177 -.255 -.286 q (4) Face - -.0006 .010 .014 .012 q a=cavitation number .383(See Figure 12 for plot of pressure distribution.)
Time and material studies of four ships from I 20 to 3500 tons in an
East German shipyard showed that 22-40 welder hour, 60 to 77 pounds
of electrodes and 880-1300 cubic feet of gases were requked per ton of ship weight. Conversion from manual to submerged-arc welding
re-suited ¡n better utilization of yard area.
Experiments with a corona-discharge torch consisting of a tungsten
electrode surrounded by nitrogen, 002, argon or hydrogen and powered
by a ¡-kw triode at 27 kc showed that the flame was too unstable for
practical use. However, tungsten and molybdenum wires, steel sheet
0.032-inches thick, refractories and quartz could be melted or welded.
-from WELDING JOURNAL
May 1960
44S A.S.N.E. Journal, August 960
y/e . (-.055)