TECHNISCHE UNIVERSTEIX Laboratorium voor
Stheepshydromechanict
1MN&
Mekelweg 2,2628 CD Delft
Terz015 - 755873 Fee015 781835THE CATHOLIC UNIVERSITY OF AMERICA
AN EXPERIMENTAL INVESTIGATION OF VISCOUS ASPECTS OF PROPELLER BLADE FLOW
A DISSERTATION
Submitted to the Faculty of The School of Engineering and Architecture Of The Catholic University of America In Partial Fulfillment of the Requirements
For the Degree Doctor of Philosophy
by
Stuart Dodge Jessup
Washington, D.C. 1989
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JeTThis dissertation was approved by Mario Casarella, Ph.D. as Director, and Y.C. Whang, Ph.D and Thomas T. Huang, Ph.D. as Readers.
Reader
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TABLE OF CONTENTS Page LIST OF FIGURES iv LIST OF TABLES viii ACKNOWLEDGEMENTS ix LIST OF SYMBOLS CHAPTER 1 - INTRODUCTION 1.1 Background 1
1.2 Classification of Viscous Flow Regions
3
1.3 Review of Previous Experimental Investigations
7
1.4 Objective of Research
11
CHAPTER 2 - EXPERIMENTAL TECHNIQUE
15 2.1 Facility 15 2.2 Propellers Tested 17 2.3 LDV System 19
2.4 Traverse Systems and the Tunnel Window Insert 24 2.5 LDV Measurement Configurations
27
2.6 Computerized Data Acquisition 28
2.7 Measurement Accuracy
32
2.8 Measurement Matrix and Test Conditions CHAPTER 3 - EXPERIMENTAL RESULTS AND ANALYSIS
65
3.1 Upstream and Downstream Time Average Flow
65
3.2 Upstream Time Varying Flow 90
3.3 Blade Surface Pressure Distributions 109
3.4 Blade Boundary Layer Flow 121
3.4.1 Results at r/R.,.0.7
122
3.4.2 Results at r/R-0.9 and r/R-0.95 124
3.4.3 Results at r/R-0.975 Near the Tip Vortex 126 3.5 Global Blade Wake Flow
154
3.5.1 General Wake Flow 155
3.5.2 Tip Flow
157 3.5.3 Hub Flow
159
3.5.4 Downstream Vorticity Field 160
3.5.5 Downstream Wake Trajectory 162
3.6 Detailed Blade Wake Flow 202
3.6.1 Mid-Span Trailing Edge Flow 202
3.6.2 General Wake Characteristics 204
3.6.3 Radial Variation in Blade Wake Parameters 205 3.6.4 Downstream Variation of Blade Wake Parameters:
Blade Wake Decay 209
3.6.5 Tip Vortex 212
CHAPTER 4 - SUMMARY AND CONCLUSIONS 236
4.1 Summary of Results 236 4.2 Conclusions 240 REFERENCES 247 iii .0.o .... ... ... -,..---..., ......,--... x . 1 ... . ... .... ...,. ... ... ... ... ... ...-...,... , . ... ...
LIST OF FIGURES
Page 1-1 Comparison of Velocity Distributions Downstream of Similar
Propellers, X/R=0.33, r/110.8 13
1-2 Propeller 4119 Looking From Upstream 14
1-3 Propeller 4119 Looking From the Side 14
2-1 DTRC 24 Inch Water Tunnel 37
2-2 DTRC 24 Inch Water Tunnel Test Section 38
2-3 Velocity Distribution Across Test Section Center 39
2-4 Propellers 4119 and 4842 40
2-5 Hub and Shaft Details for Propellers Tested 41
2-6 Open Water Test Results for Propeller 4119 42
2-7 Open Water Test Results for Propeller 4842 43
2-8 Hub and Shaft Details for Propellers Tested in Open Water 44
2-9
LDV System Optics Board 451-10 Blue and Violet Beam Standard Optics Path 45
2-11 Green Beam Fiber Optic Probe Optical Path 46
2-12 Optical Path for One Component Configuration 46
2-13 Traverse System for Two Component Standard Optics 47
2-14 LDV Optics Board and Traverse Systems 48
2-15 Schematic of Fiber Optic Probe Traverse 50
2-16 Velocity and Coordinate Description for Three Component
Measurement 50
2-17 Tunnel Configuration for Three Component Measurement 51 2-18 Alternative Measurement of Axial and Radial Velocity
Using Standard Lens Optics 52
2-19 Measurement of Streamwise Blade Boundary Layer 52
2-20 Measurement of Radial Blade Boundary Layer Using
Alternative Optics Configuration 53
2-21 Tunnel Configuration for Radial Blade Boundary Layer
Measurement 54
2-22 Data Acquisition System 55
2-23 Shaft Encoded Data Acquisition Program 55
2-24 LDV Measurement Test Matrix for Propeller 4119 61
2-25 LDV Measurement Matrix for Propeller 4842 64
3-1 Axial Velocity Distribution About Propeller 4119,
Hub Only 73
Tangential Velocity Distribution About Propeller 4119,
... .... .. ... ... . ... .... ... , .... ... . , ....
...
...
3-3 Calculated Axial Velocity Distributions About
Propeller 4842, Hub Only 74
3-4 Time Average Flow Ahead of Propeller 4119
75
3-5 Upstream Tangential Velocity Distributions 77
3-6 Axial Velocity Distribution Upstream of Propeller 4842
77
3-7 Axial Velocity Downstream of Propeller 4119 78
3-8 Three Component Mean Velocity Downstream of Propellers 79
3-9 Downstream Radial Flow Angles 82
3-10 Measured Circulation Distributions 83
3-11 Hub Boundary Layer Flow, Propeller 4119 84
3-12 Comparison of Measured and Calculated Time Average
Velocity Downstream of Propellers 85
3-13 Comparison of Measured and Calculated Circulation
88 3-14 Tangential Velocity Downstream of Propeller Showing
Blade Wake 89
3-15 Typical Shaft Encoded Velocity Distribution
Ahead of Propeller 4119 94
3-16 Velocity Vector Representation of the Flow Field
Upstream Near the Leading Edge of Propeller 4119 95 3-17 Velocity Distributions Ahead of Propeller 4119
96 3-18 Velocity Distributions Ahead of Propeller 4842
99 3-19 Near-Hub Axial Velocity and Hub Boundary Layer
Distributions Upstream of Propeller 4119 102
3-20 Radial Velocity at Inner Radii, Upstream of Propeller 4119 105 3-21 Radial Velocity Distributions Within the Hub Boundary Layer 106 3-22 Comparison of Measured and Calculated Time Varying Velocity
Upstream of Propeller 4119 107
3-23 Typical Blade to Blade Flow Through Propeller
Plane
From Inertial Frame of Reference 113
3-24 velocity Vector Field Through Blades at 0.7
Radius
From Moving Blade Frame of Reference 114
3-25 Streamwise Pressure Distribution at 0.7 Radius Derived
From Blade Surface Velocity Measurements 115
3-26 Blade Surface Radial Velocity Distributions With
Comparison to Panel Method Calculations 116
3-27 Comparison of Pressure Distribution Derived From Total
and Streamwise Blade Surface Velocities 117
3-28 Comparison of Measured and Calculated Pressure
Distributions 118
3-29 Typical Blade Boundary Layer Measurement Represented in
the Inertial Frame of Reference 131
3-30 Streamwise Boundary Layer At 0.7 Radius of Propeller 4119 132 3-31 Shape Factor and Displacement Thickness at 0.7 Radius
of Propeller 4119 135 . ... ,... .... ... -...,, ... , -. . ... ... ... .... , . . .
3-32 Streamwise Turbulence Intensity on the Suction Side
at 0.7 Radius of Propeller 4119 136
3-33 Suction Side Radial Boundary Layers at 0.7 Radius
on Propeller 4119 138
3-34 Blade Boundary Layers at 0.9 Radius of Propeller 4119 139 3-35 Shape Factor and Displacement Thickness at 0.9 Radius
of Propeller 4119 141
3-36 Blade Boundary Layers at 0.95 Radius of Propeller 4119 142 3-37 Shape Factor and Displacement Thickness at 0.95 Radius
of Propeller 4119 144
3-38 External Velocity Vectors and Streamlines in the Tip
Region of Propeller 4119 .145
3-39 Suction Side Streamwise Boundary Layers at 0.975 Radius
of Propeller 4119 146
3-40 External Streamwise Velocity on the Suction Side
of Propeller 4119 at 0.975 Radius 147
3-41 External Radial Velocity on the Suction Side
of Propeller 4119 at the 0.975 Radius 148
3-42 Streamwise Turbulence Intensity on the Suction Side
of Propeller 4119 at the 0.975 Radius 149
3-43 Streamwise Boundary Layers on the Pressure Side at 0.975
Radius 149
3-44 Shape Factor and Displacement Thickness at 0.975 Radius
of Propeller 4119 150
3-45 Composite of Radial Velocity Distribution at the Tip of
Propeller 4119 151
3-46 Estimated Tip Vortex Trajectory 153
3-47 Typical Fixed Frame Velocity Field Downstream
of Propeller 4119 166
3-48 Moving Frame Pitchline Coordinate System 167
3-49 Typical Velocity Field Downstream of Propeller 4119
Represented in the Pitchline Coordinate System 168
3-50 Fixed Frame Velocity Fields Downstream of Propeller 4119
at X/R=0.328 169
3-51 Streamwise Pitchline Velocity at X/R=0.328 171
3-52 Cross Plane Vector Field Downstream of Propeller 4119 at
X/R-0.328 172
3-53 Moving Frame Velocity Fields at X/R-0.951 175
3-54 Pitchline Cross Plane Vector Field at X/R=0.951 178
3-55 Pitchline and Radial Velocity Distributions Near the
Tip of Propeller 4119 at X/R-0.328 179
3-56 Surface Representation of Pitchline Velocity Near the Tip
at X/R=0.3t8 180
Velocity Distributions Through the Tip Vortex Core at
.. .. . , ... ...
3-58 Pitchline Cross Plane Vector Field Near the Tip
at X/R-0.328 181
3-59 Surface Representation of Pitchline Velocity Near the Tip
at X/R=0.951 182
3-60 Velocity Distributions Through the Tip Vortex Core at X/R-0.951
182 3-61 Pitchline Cross Plane Vector Field Near the Tip
at X/R=0.951 183
3-62 Surface Representation of Pitchline Velocity
Near the Hub.. 184 3-63 Pitchline Cross Plane Vector Fields Near
the Hub 185
3-64 Pitchline Vorticity Distribution in the Wake
187
3-65 Surface Representation of Pitchline Vorticity
in the Wake.. 188 3-66 Contours of Pitchline Vorticity in the
Wake 189
3-67 Distribution of Pitchline Circulation in
the Wake 192
3-68 Variation of Tip Vortex Parameters in the Wake
194 3-69 Radial Location of Tip Vortex
195 3-70 Determination of Downstream Wake Pitch
196 3-71 Angular Position of Wake With Downstream
Distance 197
3-72 Tip Vortex Pitch Trajectory
197
3-73 Distribution of Downstream Wake Pitch for
Propeller 4119 198 3-74 Contours of Pitchline Vorticity in the Near Wake of
Propeller 4842 199
3-75 Propeller Wake Fields
200 3-76 Velocity Vector Field at the Tailing Edge
at 0.7 Radius 214 3-77 Total Velocity and Flow Angle at the Trailing Edge
at 0.7 Radius
215 3-78 Derived Pressure Distribution at the Trailing Edge
at 0.7 Radius
216 3-79 Fixed Frame Velocity Distributions
Through the Blade Wake 217 3-80 Moving Frame Pitchline Velocity Distribution
Through Blade Wake 219
3-81 Comparison of Turbulence Intensity From Direct and Derived Measurement
221 3-82 Mean Pitchline Blade Wake Profiles
222 3-83 Pitchline Velocity Fields Near the Tip
223 3-84 Radial Distribution of Blade Wake Momentum Thickness
225 3-85 Radial Distribution of Blade Section Drag
Coefficients 225
3-86 Downstream Variation of Blade Wake Characteristics
at
0.7 Radius 226
3-87 Downstream Variation of Blade Wake Characteristics at 0.9 Radius 231 vii ... ... . ... , ...
3-88 Decay of Wake Centerline Velocity With Downstream Distance. .233
3-89 Wake Spreading With Downstream Distance 233
3-90 Velocity Distributions Through Tip Vortex Core 234
3-91 Variation of Radial Velocity Through Tip Vortex With
Downstream Distance 235
LIST OF TABLES
2-1 Geometry of DTRC Propeller 4119 242
2-2 Geometry of DTRC Propeller 4842 243
2-3 Thickness and Camber Distribution for DTRC Propellers
4119 and 4842 244
2-4 Load Data For Propellers 4119 and 4842 245
2-5 Specifications of 3 Component LDV System 246
... ...
... ....
:=1
ACKNOWLEDGEMENTS
This thesis effort could not have been possible without the many
contributions I have received from colleagues and friends. To them I wish to express my sincere appreciation.
I would like to express appreciation to my many colleagues at the David
Taylor Research Center who have assisted me in the development of my
career in the area of marine propellers. Mr. Robert Boswell trained me in the practical art of propellers during my early years at DTRC and has been a continued inspiration in all areas of investigation. Dr. Terry Brockett supported me in the early development of propeller flow measurement using Laser Doppler Velocimetry and motivated me to pursue this advanced degree. Also, I would like to thank Dr. William Morgan and Mr. Justin McCarthy for
their consistant support of my work in the propeller area.
I would like to acknowledge the support I received from DTRC that
permitted me to complete my dissertation. Work performed at DTRC was
primarily funded under the Navy's Independent Research (IR) program. My University program was supported by the DTRC Extended Term Training program which provided me a two year period to persue my academic goals.
The results to be presented would have been difficult to obtain without the efforts of Dr. David Frye in development of the data acquisition system for the IBM PC. The work of Dr. Frye represents possibly the best LDV data collection software in existence today.
I wish to express appreciation to my dissertation director, Professor
Mario Casarella. Dr. Casarella supervised
my work with patience and
perseverance in an area that was somewhat new to him. He asisted in the organization of the effort and followed it through to completion.
I wish to thank Dr.s Huang and Whang for taking the time to review the dissertation. Their comments improved the work and helped to formulate the
important conclusions from the results.
Finally, I would like to thank my family for their support though the long process that led to a finished thesis. My absence for many weekends
was difficult. Hopefully, in their eyes, the completion of my thesis was worth their sacrifice.
LIST OF SYMBOLS blade section chord length.
total blade section Pressure coefficient, 1-(VB/VR)2-(Vr/VR)2 (Cv)s streamwise blade pressure coefficient, 1-(VB/VR)2
propeller diameter blade section camber
maximum camber of blade section fM
shape factor, boundary layer or wake displacement thickness divided by momentum thickness,
We
iT blade section rake, axial displacement of blade section relative to blade generator line, positive aft
advance coefficient, V/nD blade number
thrust coefficient, thrust/(1/2pn2D4) Kt
K torque Coefficient, torque/(1/2pn2D5) blade section Pitch
radius
tip radius of propeller
Rn Reynolds number, (VR C)/ v, if not specified, VR based on 0.7R (RMS) root mean square value, equivalent to turbulence intensity
distance from trailing edge, along blade pitch helix blade section thickness
tm maximum blade section thickness
V freestream axial velocity aproaching propeller, advance speed VB streamwise velocity in the angle direction relative to the
moving blade coordinate system, in the wake,
= 0
VB = -V21-Inrcos0
= (Vt)m cos0 +
Vx sin.'TN lateral velocity perpendicular to the streamwise 0 direction relative to the moving blade coordinate system
VN = (Vt)m sins - Vx
cos0p
Vr radial velocity, positive outward from propeller shaft VR resultant inflow velocity to blade section,
VR= (V2 + (21Tnr)2)1/2
Vt tangential velocity, positive in the direction of propeller rotation
(Vt)m tangential velocity in the blade moving frame (Vt)m Mar - Vt
Vz vertical velocity, positive upward
Vi velocity measured in (4) direction, in fixed frame of reference
WB vorticity in the moving streamwise pitchline coordinate system,
WB - VN - 1 aVr + avN
rsino
ae
orX axial distance from propeller centerline, positive downstream also distance along chord line from leading edge of blade section
Xc fraction of chord
horizontal distance from propeller axis, positive to the right looking upstream
vertical distance from propeller axis, positive up streamwise displacement thickness
circulation fluid density
kinematic viscosity blade angular position
streamwise momentum thickness
es
projected skew angle, degrees0 LDV velocity measurement direction, angle from vertical, positive upstream
propeller blade section pitch angle
ABSTRACT
An experimental investigation of the laminar/turbulent flow in the vicinity of a rotating propeller blade was conducted using laser doppler
velocimetry. Details of the flow were measured to assess the viscous
features relative to classical potential theory and wing flow.
Three-dimensional velocity component measurements were made of the propeller blade boundary layer and wake using laser doppler velocimetry with a phase averaging technique to account for blade rotation.
The propeller blade flow was characterized by streamwise and radial boundary layer profiles. Laminar boundary layers were initiated at the leading edge with transition to turbulence occurring at the mid-chord of the blade. The midspan streamwise boundary layer resembled typical two-dimensional behavior. The radial boundary layer exhibited large outward flow near the wall in regions of laminar flow which was reduced after
transition. The outer blade boundary layer edge velocities along the blade were predicted by potential theory implying no significant viscous-invicid
interactions. The tip vortex initially formed at the blade tip and
convected over the blade surface locally distorting the blade surface
boundary layer.
The propeller turbulent wake was dominated by individual blade wakes, hub and tip vortices. The radial attached boundary layer at the trailing
edge of the blade convected into the wake, and produced significant
outward, radial flow at the wake centerlines causing a redistribution of
the classical sheet vortex. However, in the streamline direction, the
measured wakes followed typical two-dimensional turbulent wake decay laws. Tip vortex roll-up was almost complete at the blade trailing edge, causing
a reduction of the vortex sheet strength near the tip relative to
moderately loaded propeller theory. With increasing downstream distance, the vortex and the blade wake system diverged through mutual induction andlocally decayed and dispersed through turbulent dissipation.
This investigation of propeller flows supports and improves current empirical propeller wake models that incorporate distinct tip vortices and
deformed vortex wake sheets. It is proposed that improvements in
performance prediction could be made by considering the dispersion of the wake sheet, measured blade section drag coefficients, and modification of1
CHAPTER 1
INTRODUCTION 1.1 Background
Propellers have been the primary form of self-propulsion for ships for over 100 years. Aircraft have almost exclusively relied on propellers for propulsion until recent use of jet propulsion. The development of modern
aircraft propellers or prop fans has shown significant improvements in efficiency over jet propulsion and these designs are being adopted for the
next generation of air transports. Propellers produce thrust by the
production of lift from the individual blades, and therefore are part ofthe more general class of lifting surfaces which also include wings,
rudders, and sails. The propeller lifting surface is developed along a
helical surface whereas a wing is developed along a planar surface.
Marine propellers generally operate at the stern within the wake of the ship. This provides improved efficiency but significantly complicates the propeller hydrodynamics. The blade inflow varies significantly as the propeller rotates, producing unsteady lift and thrust. Also, a complicated interaction occurs between the propeller and the ship's wake. Through the years, ship and propeller designers have overcome this complex situation
through experience, good design practices , and model testing. These
efforts resulted in efficient propulsion with acceptable vibration
characteristics. Propeller theory is used to provide the basic
understanding to develop new propeller designs with a minimum of model
testing and preliminary design iterations.
Modern propeller theory is primarily based on potential theory. Vortex
lattice and panel methods are currently used in propeller design and
analysis. A review paper by Kerwin(1986) summarizes the present state of the art.
Kerwin and his colleagues at MIT have formulated lifting surface
computational procedures for propeller design and analysis with increasing
sophistication since the early 1960s. These numerical methods have been
primarily based on vortex lattice models, representing each blade as a
condition was enforced on the meanline surface to arrive at the strength of the vortex lattice elements. Blade thickness was represented in a two-dimensional stripwise sense. Early procedures only modeled the blades, and incorporated a simple blade wake model where the vortex segments continued downstream at a specified pitch angle with no wake contraction.
Current procedures, specifically the analysis program, PSF-2, written by Greeley
and Kerwin (1982) incorporate a more sophisticated wake model drawing on
empirical data to include the tip vortex roll-up and iterative pitch
alignment in a transition wake along with a set of hub and tip vorticies in
the ultimate wake. Wang (1985) added the hub to the propeller vortex
lattice model. The most recent propeller computational program developed at MIT by Kerwin(1987) is a panel method that includes the propeller blades
and hub, and incorporates the same wake model as Greeley. This improved
code overcomes the shortcomings of the previous vortex lattice methods in properly modeling the thickness of the blades especially near the hub and blade leading edges.
Other panel codes have been developed in recent years with some
variation to the latest MIT program. Hess and Valarezo(1985) developed a propeller and hub panel code that utilized a simplified downstream wake of a pure helix in the transitional wake and a semi-infinite cylindrical wake as an ultimate wake model. Vaidanathan (1984) and his colleages have also developed a panel code for marine propellers. The wake model for this code is relatively simple with the wake sheets convected back along pure helices. This computational program, VSAERO, has been used at DTRC by Yang (1987,1988) to correlate with existing propeller blade measurements by
Jessup (1986). These comparisons showed excellent correlation, except in the tip region, when the hub was included in the model.
All of these programs should perform similarly when properly modeling the blades and hub for propellers operating in uniform inflows. Variations
will occur with paneling distributions near the edges of the blade,
different application of a Kutta condition, and various representations of the propeller wake. The accuracy of potential flow predictions has now
reached a level in which, for marine propellers of moderate or light
loading, viscous flow interaction effects warrant consideration for any significant improvements in state-of-the-art propeller flow predictions.
"41
Compressible Euler solvers have already been developed by Yamamoto (1986) and Agarwal(1986) in the aerodynamic field for prop fans and helicopter
rotors. An Euler solver for incompressible flow for marine application may permit correct consideration of inflow vorticity and vorticity convection
in the wake, but presently no working programs exist. Propeller-hull
interaction, and the complexities of the propeller inflow require this consideration.
Few viscous flow codes have been developed for marine propellers.
Groves (1981,1984) developed a momentum integral boundary layer
computational procedure for rotating blades, and later, a finite difference procedure. A partially parabolic procedure by Stern et al.(1986) represents the blades as body force distributions. Viscous field solutions including detailed blade flow have not yet been developed.
1.2 Classification of Viscous Flow Regions
The various viscous/inviscid interaction regions of the propeller flow can be identified as the flow approaches and passes through blades of the propeller. For moderately loaded propellers, regions of the flow can be
identified as predominately viscous or potential flow.
The viscousdominated regions will be discussed relative to the issues addressed in
this research investigation.
Propeller Inflow
For the case of a propeller operating in uniform inflow, the flow is purely inviscid potential flow. The idealized case of purely uniform inflow only occurs in the model testing stage of ship design. Each model propeller is tested over a range of operating conditions in open water, driven from a
long extended shaft in a towing basin. Results from these open water tests
are used to evaluate model propulsion. Therefore understanding the
propeller flow in this configuration is important. However, this flow condition is the simplest to predict.
Hub flows for even the simplest case of uniform inflow should be
considered. General hub shapes will produce a potential flow perturbation that will influence the blade inflow. This effect can easily be predicted with hub modeling. The boundary layer flow over a spinning hub can provide a complicated inflow to the root sections of the blades. The hub inflow boundary layer can be significant for the case of a propeller driven by
3
the shaft which can extend far upstream. An example would be a propeller driven from upstream in a water tunnel. In this case the hub boundary layer can extend up to 10Z of the tip radius. This could have profound effects on
horseshoe vortex generation about the hub, and general secondary flow about the root of the blade.
Most marine propellers do not operate in this flow regime. In the
case of submarines and merchant ships,
the inflowis highly three
dimensional and viscous, with the propeller almost entirely inbedded in the
hull boundary layer. Most high speed naval surface ships drive their
propellers with inclined shafts open to the flow below the hull. In this case, the propeller operates in a primarily potential flow field, but the shaft inclination causes the propeller to experience unsteady operation. The shaft and the supporting struts generate localized wakes that convect into the propeller.
These practical configurations cause complex unsteady flow phenomena and are beyond the considerations of this fundamental investigation. This basic study of the physical aspects of the viscous flow in the near wall regions of the blade and wake will address the idealized inflow of the open water test. This minimizes inflow uncertainty so that dominant real flow effects can be more easily isolated.
Blade Leading Edge Flows
Real flow effects begin at the blade leading edge. A stagnation point
can occur at some point along the leading edge with stagnation lines
extending from the point inboard and outboard along the edge. Flow from
these lines begins the boundary layer development on each side of the
blade. Most marine propellers are designed to operate, in the average sense, at ideal angle of attack. For this case the boundary layer develops
in a strong favorable pressure gradient typical of 2-d stagnation point flow, and no flow separation occurs. When the propeller is operating off design , high velocities around the leading edge followed by an unfavorable
pressure gradient will cause laminar flow separation. At conditions far
from design, complete separation over the entire blade can occur, while for less extreme loadings, the flow reattaches developing a turbulent boundary layer. Studies of this flow have been performed primarily due to interest in leading edge cavitation. Kuiper(1981) has studied the scaling of blade
layer. The detailed mechanics of this flow are unknown due to the small scale of typical model propellers. Greeley (1982) attempted to model the leading edge flow with a local tip solution which allowed vorticity to be
shed from the leading edge simulating flow separation.
Swept wingexperiments, reviewed by Greeley showed strong effects of Reynolds number and leading edge swept angle.
The present investigation was restricted to propeller operation at design condition only. For this case, over most of the blade, the leading
edge flow is void of separation and initial boundary layer flows can be assumed as stagnation flow. Detailed measurements at the leading edge are very difficult with typical model propeller geometry. Limited positioning
accuracy, surface reflection, and measurement volume size restrict
measuring flows around the tip in detail.Mid-Span Blade Flows
The mid-span regions of the blade, when void of separation, are
characterized by three dimensional boundary layer flow. This flow regime is perhaps the simplest, fortunately, since there the majority of the blade load is generated. Propeller rotation affects the boundary layer flow along
with the general potential flow field.
This flow was calculated by
Groves(1984) for simple propeller geometry Blade flow separation usually
occurs towards the trailing edge of the blade. The flow separation is a
complex three-dimensional phenomenon.
Trailing Edge Flows
Trailing edge flows comprise the merging of the blade boundary layer flows on either side of the blade. In potential flow theory, this flow is
addressed with the Kutta condition. In reality the blade boundary layers at the trailing edge are relatively thick, as compared to the trialing edge thickness and the condition of constant pressure at the trailing may not
hold. Propeller blades often have discontinuous chisel shapes at the trailing edge which produce local flow separation at the discontinuity.
This feature complicates the trailing edge flow. The propeller tested has continuous rounded trailing edges producing a relatively simple flow. The LDV measurements performed in this investigation provide good detail in this region.
Tip Flows
Tip flows are one of the most complicated flow regions on the blade. Near the tip the leading edge flow at design condition will produce a stagnation line out along the leading edge. Flow will be attached around the leading edge. Radial flows increase as the tip is approached with flow tending to go around the tip. At some point the radial flow around the tip cannot remain attached through the adverse pressure gradients around the
tip and the flow separates at the tip. At that point the tip vortex
originates.
The development of the tip vortex seems to be greatly dependent on the blade geometry in the tip region. For blades with zero chordlength at the tip, the vortex starts at the outermost tip and travels over the suction side of the blade moving inboard. For blades with significant skew, the tip is moved downstream relative to the inboard blade sections, altering the tip vortex blade flow interaction. Also, blades with finite chordlength at the tip will generally cause the tip vortex separation to occur at the tip trailing edge. The effect of tip geometry will be addressed to some extent
in this investigation.
After initial vortex formation at
the point of blade surfaceseparation, the "roll-up" process begins where vorticity from the blade "vortex sheet" convects and rolls up into the tip vortex. This process is
highly viscous at the vortex core center, and primarily a general flow convection process away from the core. Understanding of this process for a typical marine propeller will also be examined from the experimental data.
Mid-Span Wake Flows
The wake flow in the mid-span of the blade is characterized by the
three dimensional convection of
theblade wakes downstream of
thepropeller. The blade wakes decay and spread as they convect downstream. The radial velocity distribution which was generated by the three dimensional flow over the blades is important in distorting the sheet and convecting
vorticity toward the tip and hub.
This flow was measured
in thisinvestigation and will be reported in considerable detail.
7
blade hub intersection. This flow is also very complicated involving hub boundary layer inflow, the blade boundary layer, possible flow separation at the intersection, and vortex development along and downstream of the blade. This flow was measured to some extent, with detailed flow evaluated
primarily in the wake. Again, the configuration
tested utilized an
essentially infinite hub downstream. Therefore, the formation of a single hub vortex does not occur, but a separate vortex associated with each blade was observed.
1.3 Review of Previous Experimental Investigations
Previous flow field studies on propellers can be distinctly separated
by the development of Laser Doppler Velocimetry. Early work on marine
propellers focused on the tracking of tip
vortex trajectories whencavitation occurred. Lifting surface calculation procedures had been developed during the 1960's,
but limited knowledge existed
for thedownstream wake of the blades. Most lifting surface models assumed that the wake was convected downstream at the induced pitch angle determined from a
lifting line model of the propeller.
At MIT, Loukakis(1971) made the first attempt to measure and predict the structure of the downstream wake.
Propellers were operated in a water tunnel and the tip vortex cavitation was generated to track its pitch and radius in the wake. Calculations of the tip vortex trajectory
were made
from a model of helical vortex lines. Loukakis observed
significant
contraction of the tip vortices downstream of the propeller. He believed that a relatively short transition wake region occurred where the trailing vortex sheet rolled up and contracted, followed by an ultimate wake region made up of individual tip vortices of constant radius and pitch. Loukakis
also observed a very complex transition region where wakes from different blades combined. This qualitative understanding of the flow was entirely
based on observations of various forms of cavitation generated by the propeller.
Later, Kerwin(1976) and Cummings(1976) extended Loukakis's work by
performing further measurements of
the tip vortex radius and pitch
downstream of the propeller. The tip vortex pitch near the blades and far downstream was significantly less than the moderately loaded lifting line
model predicted. This apparently verified that tip vortex rollup was
important in modeling the flow.
The first laser doppler velocimetry measurements about a marine
propeller were made by Min(1978) and provided further insights into the
propeller wake. The LDV system at the MIT water tunnel was a one component forward scatter system measuring axial velocity ahead of and behind the
propeller operating in the tunnel. A tracker was used to process the
measurements at a sufficiently high enough data rate so as to assume a continuous analog signal that could be waveform averaged via a once per
revolution trigger on the shaft. These measurements are considered landmark
in providing the first quantitative time varying velocity measurements
about an operating propeller. The measurement spatial resolution was
limited, but it was sufficient to draw numerous conclusions concerning the
flow and the validity of the potential flow model. Min(1978) determined
distributions of slipstream radius, tip vortex pitch, and extent of roll-up for a series of propellers with varying skew. These wake characterizations were derived with crude techniques and limited measurements of the details of the flow however,they have become standard empirical settings in the MIT wake model. Min also demonstrated the ability of the MIT potential flow
codes to predict the potential flow regions of the flow upstream and
downstream outside the slipstream of the propeller. Finally, Min identified
the viscous wakes shed by the blades which led other investigators to
measure the wakes in more detail.
The next propeller flow field study was also performed at MIT by
Kobayashi(1981). This work was an extension of Min's study where the
viscous wake downstream of the blades was measured with some detail. The
single component LDV system was used, but by rotating the optics and
repeating measurements at the top and side of the propeller disk, three
components of velocity were obtained in a non-simultaneous fashion.
Measurements were made downstream of the propeller to derive the viscous drag of the blade sections. From the measurements, the vorticity in the
wake was calculated by making four measurements about a central point to calculate velocity gradients at the central point. From the vorticity, and assumptions about the flow , section drag coefficients were obtained.
Kobayashi (1981) developed computerized data acquisition to replace
the analog wave averaging system. This system collected data through an
analog to digital converter which assumed continuous signals from the LDV
the tracker will not follow the flow. This problem may have effected
Kobayashi's results, especially for the blade wakes.
As a check on this effect of data acquisition was made
with Kobayashi's results
usingsimilar propeller geometries,
andmeasurement locations downstream of the propeller. The propeller in this
study was a three bladed unskewed propeller, DTRC Propeller 4119, while
Kobayashi's results were obtained with DTRC Propeller 4381, a five bladed
unskewed propeller. Both measurements were made at approximatey 0.33R
downstream of the propeller centerline at 0.8R radius. Some variation in blade wake characteristic will occur due to differences in blade section Reynolds number,and helical distance from the blade trailing edges, but
this comparision is considered reasonable. The comparison is shown in Figure 1-1. Note that the sign conventions used are those of Kobayashi for comparison purposes. The velocity variations with blade angular position are similar, but are better defined through the blade wake in the present study. The largest discrepancy occurs in the tangential velocity which contains the major component of the streamwise blade wake deficit. It is unclear what effect the smoothing out of the wake gradients would have, but some reduction in calculated vorticity would be expected. Similar vorticity calculations were made in this investigation.
Despite this problem with Kobayashi's data collection process, these
measurements were the first three component flow field
measurementsdownstream of the propeller. The primary results showed a complex wake
field with significant radial velocity variations in the wake which in
potential flow models is represented by a vortex sheet. This implied that complete wake roll-up does not occur in the near wake, but persists well downstream.
After Kobayashi's work, numerous other investigators developed LDV
systems for flow measurements about operating propellers. Billet(1987) conducted LDV measurements about marine propellers with the inclusion of turbulence measurements derived from the rocs of the ensemble average of data collected at each discrete anglular position of the propeller. High
turbulence regions were shown in the wakes
ofthe blades. Similar
measurements were made by Cenedese(1985) in a water tunnel. Kotb and
Schetz(1986) measured the wake flow behind a propeller operating in a
nonuniform
shear flow in air. The measurements were made with hot wiresstress measurements. Turbulence was also shown to be localized at the blade wakes but higher levels occurred near the hub and tip associated with the tip and hub vortex structure. With the hot wires, no data could be obtained inside the blade passage. Other LDV measurements about aeroplane propellers have been conducted by Serafini(1981), Lepicovsky(1984) and Sundar (1985).
All of these experimental investigations have identified the blade wake, hub, and tip regions as complications in the flow with high turbulence, but detailed wake measurements had not been made. Jessup(1984) measured the streamwise blade boundary layers on a marine propeller demonstrating the
similarity of the blade flow mid-span to two-dimensional blade section
flow. Radial or wake flows were not measured. Recent
studies by
Schetz(1988) obtained wake measurements on a marine propeller operating in &wind tunnel using hot wire techniques.
The field of turbomachinery also has studied the flows about turbine blades. The field is quite extensive, but noteworthy studies are the work of Lakshminarayana(1974,1982) and Reynolds(1979). Measurements were made as early as 1974 of the blade row wakes using stationary hot wire probes. In 1979, the wakes were measured with a probe that rotated with the blade row. In 1982, measurements were made of the blade boundary layers with the
rotating probe. These measurements included three components of velocity, turbulence and Reynolds stress. These results have been used to develop viscous flow codes most recently by Warfield and Lakshminarayana(1987).
Unfortunately, the turbomachinery problem is significantly different from the open propeller. Some of the differences are the suppression of tip flow, high freestream turbulence, higher blade loading, number of blades, and upstream and downstream blade interactions.
There are a variety of other related viscous flows in which detailed experimental data exists. These include two-dimensional airfoils, rotating bodies , rotating disks, vortex flows, wings, and wing body juncture flows.
Data has been obtained in the wake region of two dimensional airfoils characterizing the mean and turbulence quantities. Hah(1980) measured the wake behind a NACA 0012 airfoil at various angles of attack with analysis of the decay of the mean and turbulent quantities with distance downstream. Yu(1981) made similar measurements for a NACA 63-012 airfoil concentrating
on the near wake less than 101 chord downstream. In each case, Reynolds stress was measured. These studies can provide a baseline of comparison
Data obtained on rotating bodies provides insights to the blade
boundary layer characteristics. Lakshminarayana (1972) measured mean and limited turbulent quantities on a blade of large chord rotating in an annulus. These measurements were very idealized, being an extension of rotating disk.
1.4 Research Objective
The objective
of
this research was to determine experimentally the detailed viscous/inviscidflow
about the bladeof
an operating propeller. This study addressed the caseof
a propeller operating in a uniform inflow with low levels of freestream turbulence. Propeller loading was relatively low, typical of a marine propeller, so that strong viscous effects were restricted to blade and hub boundary flow and the individual blade wakes convected downstream. For this case the interesting aspects of theflow
become the three dimensional blade boundary layers, the tip vortex,near hub vortex, and wake
flow
downstream of the blades. Mostof
the flow field near the blades remains effectively inviscid, interacting with the regions
of strong vorticity and turbulence.
The propeller flow field was measured with a three component laser
doppler velocimetry (LDV) system about a model propeller operating in a
water tunnel, as shown in Figure HT and 1-3. The propeller was driven from
downstream operating in a uniform inflow at its design condition. LDV
measurements were phase averaged to the angular position of the rotating propeller to obtain mean and flucuating velocity distributions relative to the individual blades. Measurements were obtained upstream, downstream, and through the propeller disk. The measurement resolution was sufficient
to define the blade boundary layers
and
blade wakes. A three bladed marinepropeller model of conventional geometry was used for this study.
Some limited measurements were also performed on a model representing a typical modern marine propeller design.
The results of these experiments were analyzed from the following
perspectives. From a scientific point of view, the characteristics of
rotating blade flows are unique because of the general three dimensionality of the flow, the effects of rotation, and the helical nature
of
the wake. Comparisons of theflow
can be made with low aspect ratio wings, line vortex flow, rotating disk flow, and two dimensional airfoil flows.A second perspective for analysis is from a propeller designer's point
of view. Modern propeller design relies heavily on numerical procedures to
design full scale geometry and predict performance. Most computational methods are based on potential flow , where an account of viscous effects
is through simple account of blade drag. Results from this experimental
investigation can improve the empirical corrections to present potential flow codes. Also, experimental data quantifying the detailed viscous nature
of the flow will help in the future development of full Navier Stokes solutions to complex propeller flow.
0.2
VrAt Vt/V Vx/V-0.4
0.0
0.6
1.5
0.9
13 l 1 \BLADE ANGULAR POSITION
Figure 1-3 Comparison of
Velocity Distributions Downstream ofSimilar
Propellers, X/R0.33, r/R.-0.8 _ ... ...
PROP 4119__\
Z
\
..-.."--
.-
\
_-\
PROP 4381. KOBAYASHI(1981)FIJ74
Figure 1-2 Propeller 4119 Looking From Upstream
15
CHAPTER 2
EXPERIMENTAL 'TECHNIQUE
2.1 Facility
The facility used for these experiments is the David Taylor Research Center (DTRC) 24 inch Variable Pressure Water Tunnel. The water tunnel was constructed in 1940 primarily for performing
cavitation tests on model propellers. A schematic of the tunnel is shown in Figure 2-1. The tunnel
has an open test section in which the flow enters and exits an enlarged
test section chamber producing a 24 inch diameter flow with
a peripheral shear layer extending to relatively still water within the chamber.
The test section is shown in Figure 2-2.
Propellers can be driven from upstream or downstream shafting which
extend out of the tunnel to dynamometers and motor drives. The upstream
drive utilizes a 25 HP dynamometer while the downstream drive can be driven by a 150 HP or 10 HP dynamometer system depending on the propeller size.
The 150 HP system is driven through a rigid 2.25 inch diameter shafting
system. This system was selected for these experiments because of its high torsional stiffness required for the measurement of the propeller angular position The disadvantage of this arrangement
was the low accuracy of the thrust and torque measurements resulting from operating at approximately 5% of the rated loading of the dynamometer.
The quality of the mean flow in the test section is considered average
when compared to typical modern flow facilities. Figure 2-3 shows the
distribution of mean axial
velocity,Vx' and vertical velocity,Vz' horizontally across the center of the test section at the nominal test flow speed of 11 feet/second (f/s). The axial
velocity shows a retardation of
the flow in the center of the test section, which appears to be due to
potential flow effects of the upstream contraction and entrance nozzle. The vertical velocity distribution shows a slight upward component of the flow, largest at the tunnel center. The cause of this is unknown but could be due to the asymmetry of the test chamber about the mid-horizontal plane. The
inflow can be considered uniform to within 1%, which is sufficient for the experiments to be described.
The present impeller drive system controls the impeller rotation speed to a relatively low accuracy of 1%. The water speed in the test section
varied linearly with impeller rotation speed producing a similar 12
accuracy on tunnel speed. A typical time history of the impeller RPM shows a constant rpm for a period of 5 to 30 minutes followed by a 1% drop in RPM followed by a slow increase back to the original value over a 5 to 10minute period. This behavior caused problems when performing automated
measurement traverses across the test section. During the test a high
resolution encoder and counter was installed on the impeller so that its rotation speed could be monitored. During runs, the impeller speed was either manually adjusted to maintain constant flow in the test section or measurements were discarded if the impeller speed changed more that .25% of
its nominal value.
The quality of the turbulence characteristics of the test section flow is relatively poor when compared to other flow facilities. At typical test flow speeds of 8 to 11 f/s the free stream turbulence was measured to be at best 1.6% of the freestream velocity. This value was relatively high when compared to other modern facilities.
Fortunately, for these tests addressing propeller flows, the proper representation of turbulence quantities should be made from the moving
blades frame of reference. The effective flow speed across a specified blade section is referred to as the resultant velocity, VR,
VR = ( V2 +(211-nr)2)0*5
V - advance speed or in this case tunnel flow speed ms, propeller rotation speed, rps
r - radius
Also, with the advance coefficient, J V/nD, the ratio,
VR/V -
el
+ (U(r/R)/J)2)°'5freestream turbulence in the blade moving frame is reduced to 0.67%, which is relatively low.
2.2 Propellers Tested
Two model propellers were used for this study. Most measurements were
made with DTRC Propeller 4119, a three bladed propeller of relatively
simple geometry previously displayed in Figures 1-1 and 1-2. Limited
measurements were also made with DTRC Propeller 4842, a five bladed, skewed propeller representing a modern marine propeller geometry. Figure 2-4 shows photographs of these two propellers including the fairwater, hub and shaft geometry used during these tests. As mentioned earlier, these propellers were driven from downstream. The tabulated design geometry for these two
propellers is presented in Tables 2-1 ,2-2 ,and 2-3. The hub and shaft details for the two propellers is shown in Figure 2-5.
Propeller 4119 is a 12 inch diameter, three bladed propeller of
relatively simple geometry. The propeller was designed by Denny (1968), for
uniform inflow as a double thickness version of Propeller 4118. The
propeller was designed with state of the art lifting surface techniques at that time. The design condition of the propeller occurs
at an advance coefficient ,J 0.833 with a thrust coefficient, Kt of 0.154. At that
condition, when operated in uniform flow, the blade sections are designed
to operate at shock free entry, ideal angle of attack. This produces
a
relatively well behaved leading edge flow where the forward half of the chord sees a favorable pressure gradient in respect to the blade boundary
layer growth. The propeller has a near optimum load distribution which
tends to load the hub and tip region higher that a typical modern marine propeller. The propeller has relatively constant pitch with no skew or rake as shown in Table 2-1. This results in a relatively straight blade which is very conducive to LDV measurements of the surface flow on the blade. LDV
measurements can be made of the entire blade surface using the optical
configuration to be be discussed later in this report. Propeller 4119 is a relatively old propeller which was hand filed from a monobloc casting using templates and gages. Therefore the accuracy of model was checked using a coordinate axis automated measuring machine and found to sufficiently match the design geometry.
Propeller 4842 is a five bladed propeller with characteristics of a
typical modern marine propeller. A large hub diameter and nonlinear skew
17
-distribution is indicative of a typical controllable pitch propeller. The propeller was numerical control (nc) machined with monobloc construction and therefore represents a state of the art high accuracy model. The radial load distribution is somewhat reduced at the hub and tip from optimum. The
design advance coefficient is J=0.905 with a relatively high thrust coefficient of 0.305. The propeller is a wake adapted design meaning that the specified inflow is not uniform but a specified distribution associated with a given ship. For this case, the radial variation of axial inflow is slight, increasing approximately 10% from hub to tip. The propeller blade sections were .designed for ideal angle of attack in the specified wake. Testing or analyzing this propeller with a uniform inflow, for this case
should not significantly alter the blade surface flow from the design case.
Both of the tested propellers were designed with no hub model.
Therefore the existance of the hub may alter the blade section inflow significantly for the hub configurations shown in Figure 2-5. The effect of the hub on the measured flow will be discussed in a later section of this
report. The ability to design the hub and propeller within a lifting
surface design code has been demonstrated by Wang(1985).
Both of the propellers have been tested in open water for thrust and torque characteristics over a range of advance coefficients. These tests
were performed in the MAC towing basin. The results of these tests are
shown in Figures 2-6 and 2-7. Also shown is the comparison of the measured results to the design values at design J. The hub configurations for these tests were somewhat different than those shown in Figure 2-5 and are shown
in Figure 2-6. Table 2-4 summarizes these load results. The open water
tests are conducted with and without the blades on the hub of the
propeller. The data shown in Figures 2-6, and 2-7, and Table 2-4 representsthe measured loads of the propeller minus the measured loads of the hub
alone.
The open water test data show fairly good agreement with the design
values. The design values represent the calculated thrust and torque from
lifting line calculations. The final propeller pitch and camber
distribution is calculated from lifting surface procedures to produce the design thrust and torque. If the the propeller design inflow is reasonably uniform, as it is for these propellers, then the openwater results should
openwater results will be effected by the hub and shaft configuration. For small hubs, traditionally these effects are believed to be small, but for
large hub propellers like Propeller 4842, these effects could be
significant.
Two countering effects of hub influence the resulting loads in the open water configuration. One is the image effect of the blades attached to the hub. Wang(1985) showed that inclusion of the hub will cause the blade sections near the root to generate additional loading. The other effect is the perturbation of the incoming flow as in passes around the hub. As an example, the ellipsoidal hub of Propeller 4842 will cause a relatively large augmentation of the axial inflow to the hub. This tends to decrease the loading of the root sections of the propeller. These two effects oppose each other and could cancel depending on the shape of the hub and the blade geometry near the root.
The effects discussed above are not considered viscous related
, but
must be considered when attempting to sort out the real flow performance of
the these propellers. The open water results are considered the
most accurate load characteristics, since the measurements in the 24 inch water tunnel were made at a small fraction of the load rating of the dynamometer.
2.3 LDV System
The LDV system used was a TSI Inc. dual beam on-axis backscatter system that was configured as a one, two and three component system for
various portions of the test. The configuration was changed depending on
whether measurements were being made near the blade surface or in the wake. The first two components of measurement were made using conventional lens optics entering the tunnel from the side, while the third
component was obtained using a TSI fiber optic probe mounted at the bottom of the tunnel test section.
The requirements for the measurements of the flows near the operating propeller were to maintain small measuring dimensions relative to the large flow gradients near the blades. Measurement volume size on the order of
0.003" or 0.075= was necessary to resolve the blade boundary layers and
wake details. A system to measure the streamwise velocities near the blades
had been developed earlier by Jessup(1984) to measure streamwise blade boundary layers utilizing the green 514 rim wavelength line of an ion-argon 2 watt laser. In 1985 an experiment was conducted to measure radial blade
boundary layers using the one component system. In certain aspects, these
measurements were superior to the present study and will be discussed.
The system was later expanded to two components using the green and blue
(0.488nm) lines to measure axial and tangential velocities about the
propeller. The final configuration used for these tests expanded the system further to three components using the violet (0.476 nm) line and a fiber optic probe. The final system will be described first.
Laser and Beam Separation
The three component system was a modified and expanded TSI Inc. System 9100-7 four beam, two color LDV system. The standard configuration of a
green and blue two color arrangement was expanded to a green beam fiber
optic one component system and a blue and violet beam system analogous to
the original green and blue 9100-7 system. Figure 2-9 shows a simple
schematic of part
of
the LDV breadboard arrangement. The optics weretightly pack on a 36"x 60" aluminum surface honeycomb sandwiched
breadboard. This was necessary to fit the system within the observation
room attached to the test section of the tunnel. A 2 Watt Lexel Ion-Argon Laser was used, operating in multiline mode. The beam was color separated
into multiple beams using standard TSI hardware . The green beam was
directed into the first set of optic modules for the fiber optic probe. The blue and violet beams were directed into the standard 9100-7 optics train as shown in Figure 2-9.
The etalon temperature control was used to adjust the distribution of power between the three beams from the factory setting for green ,blue,
and voilet of
78, 14, and 8 74 respectively to 60, 29, and 11 74respectively. This provided more power for the weakest violet beam. Part of the reasoning for the present arrangement was due to the large attenuation
of power through the fiber optic system. Therefore, the green beam was
selected for the fiber optic probe because it contained the largest
fraction of power. The green transmission beams were attenuated through thefibers to 1/4 the incoming power. This maintained relatively equivalent power for all three components. Another reason for the beam selection was the order of the beam split permitted the use of standard available mirrors used within the color separator box.
collection rates that was annoying at times. In the future, this problem should be avoided and may require running without the etalon, as has been done before without serious problems.
Standard Two Component Optics Path
Figure 2-10 shows a schematic of standard optics path for the two color, blue violet optics. The blue beam entered the center of the modules and was split into two coherent beams in the vertical plane. The violet
beam entered to the outside of the blue beam and was displaced to the
center of the module after the blue beam was split. The violet beam passed through a polarization rotator which oriented the beam's polarity to the vertical plane. The violet beam was then split into
two beams in the
horizontal plane. One of the blue beams was frequency shifted through
a
bragg cell which permitted the blue beam set measuring vertical (or for this configuration, tangential) velocity to distinguish flow direction.
A beam steering module was used to steer the four beams to cross at the same point. The beam stop blocked the extraneous beams that exit from the brag cell. The 22 mm beam spacers reduced the beam separation from 50
mm to 22 mm for entrance into the beam expander. The beam expander expanded the beam diameter from typically 1 mm by a factor of 2.27 and returned the
beam
separation to 50 mm. The four beams passed through two tranverse
system mirrors to the final focusing lens. Measurements were made
with 250 and 309 mm focal length lenses.
The unusual feature of the standard optics path was the use of
single receiving module to receive the returned scattered light
from both
blue and violet beam sets and direct it to a single photomultiplier.
Separation of the doppler signals from each component was performed through
band pass filtering. The blue beam, vertical component was frequency
shifted by 40 Mhz,
and high pass filtered before
the signals were
downshifted for processing. This removed crosstalk from the the violet beam doppler signals. The doppler signals from the the violet beams lowpass
filtered the blue beam signals using the counter processor filters.
For this configuration, the filtering mirror normally used with the receiving module was removed. Originally, a color separator incorporating
a dichroic mirror was procured to separate the blue and violet received light,
similar to a TSI model 9145, but the separator suffered from very
poor blue line
transmission and was not used. The single receiving module arrangement
proved to work very successfully. The only disadvantage was crosstalk that occurred with the green line from the fiber optic probe. This was overcome by offsetting the beam crossing of the green beam from the other components by typically 0.2 mm.
Fiber Optic Component Path
The fiber optic probe optical path was configured as a standard TSI one component fiber optic probe system as shown in Figure 2-11. The green line beam entered the optic modules through a polarizing rotator to set the
polarization to the vertical. The beam splitter split the beam into two
beams in the horizontal plane. One beam was frequency shifted through the brag cell module. The beams extended through a spacer separating the extraneous shifted beams, and avoiding their interference with the main
beam at the fiber coupler. The two beams passed through a beam translator which provided lateral adjustment of the beams into the fiber coupler. The 9262 optical coupler provided final lateral adjustment and focusing of the beams into the two transmitting beam single fiber cables. These cables entered a single waterproof jacketed cable which connected to the probe. Within the probe, the transmitting beams were focused and exited a flat
glass window to intersect 180 mm (7.09") from the probe end (in water). Receiving optics within the probe focused the received scattered light back through a third optical fiber connected to a standard TSI photo multiplier.
Performance of the System
The overall performance of the three component system was less that optimum due to the performance of the fiber optic probe. Originally it was believed that the performance of each component would be well matched, but when tested the fiber optic probe performance was well below the standard two component system. Table 2-5 summarizes the measuring volume sizes and
relative signal to noise ratio, SNR. The standard optics resulted in
measuring volume dimensions 2 to 3 times smaller than the fiber optic
probe. Also the relative SNR was four to eight times higher for the
standard optics.
The use of
the fiber optic probe permitted simultaneous three
component measurements. The standard lens optics measuring axial and
tangential velocities utilized the 250 ram lens. With this arrangement the fiber optic probe measured the third component, the radial velocity. The
optics to measure axial and radial velocity. This arrangement permitted
potentially higher quality radial velocity measurements over the fiber
optic probe, but measurement sets had to be repeated to obtain three
component measurements. Further discussion of these tradeoffs will be made in a later section when also considering the orientation of the measuring volume relative to the highest flow gradients, and extent of measurement
domain.
One and Two Component Systems
For some of the test period the three component system was
reconfigured as a one or two component system. Configuration as a two
component system was easily performed by simply blocking the green line
within the color separator box for the fiber optic probe and operating the standard lens optics alone.
The one component setup was used to measure velocity very close to the rotating blade surface within the blade boundary layer. This required that the plane in which the transmission beams were contained be rotated about the optical axis, and this plane be tangential to the blade surface. The optical path for this configuration is shown in Figure 2-12. One additional feature of this arrangement was the rotating mounts used at each end of the optical path. These permitted the modules between them to rotate about the optical axis. This would change the measurement direction within a plane perpendicular to the optical axis. Also shown in this configuration is a
field stop module,which was used to spatially filter the received light by focusing it through a pinhole aperture. This module was marginally useful in improving the signal quality when the measuring volume was close to a
solid surface, i.e.,
the blade or hub.
Further discussion of this
configuration relative to the blade geometry will be discussed in the next section.LDV signal processing
The doppler signals output from the LDV system were processed with TSI 1990C counter processors. The counters were operated in single measurement
per burst mode validating measurements with eight cycles through the doppler burst. The counters
are digital output devices which upon
validation of the measurement generate a data ready pulse and 12 bit
mantissa and 4 bit exponent digital output of the period of the eight