VAPOR GENERATOR  FEED PUMP



      FOR RANKINE  CYCLE



AUTOMOTIVE PROPULSION SYSTEM



      (CHANDLER EVANS)
     Colt Industries

     Chandler Evans

     Control Systems Division
            WEST HARTFORD, CONNECTICUT 06101

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APTD - 1357
VAPOR GENERATOR FEED PUMP
FOR RANKINE CYCLE
AUTOMOTIVE PROPULSION SYSTEM
(CHANDLER EVANS)
CHANDLER EVANS REPORT NO. R-679-5
U.S. ENVIRONMENTAL PROTECTION AGENCY
Office of Air and water programs
Mobile Source Pollution control programs
Ann Arbor, Michigan
48105

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APTD - 1357
VAPOR GENERATOR FEED PUMP
FOR RANKINE CYCLE
AUTOMOTIVE PROPULSION SYSTEM
(CHANDLER EVANS)
prepared By
R. M. Riordan
Approved By
J. M. Maljanian
Chandler Evans Inc
West Hartford, Connecticut
06101
Contract Number: .68-01-0430
EPA project Officers
,
W. Dyer Kenney and Kenneth F. Barber
prepared For
U.S. ENVIRONMENTAL PROTECTION AGENCY
Office of Air and Water programs
Mobile Source pollution control program
Advanced Automotive Power Systems Development Division
Ann Arbor, Michigan
48105
December 1972

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The APTD (Air Pollution Technical Data) series of reports
is issued by the Office of Air and water programs, u.s.
Environmental Protection Agency, to report technical data
of interest to a limited number of readers. copies of
APTD reports are available free of charge to Federal
employees, current contractors and grantees, and non-
profit organizations - as supplies permit - from the Air
Pollution Technical Information center, U.S. Environmental
Protection Agency, Research Triangle park, North carolina
27711, or may be obtained, for a nominal cost, from the
National Technical Information Service, u.s. Department
of Commerce, 5285 Port Royal Road, springfield, virginia
22151.
This report was furnished to the u.s. Environmental
Protection Agency by Chandler Evans, West Hartford,
Connecticut, in fulfillment of Contract Number 68-01-
0430. The contents of this report are reproduced
herein as received from Chandler Evans. The. opinions,
findings, and conclusions expresses are those of the
author and not necessarily those of the Environmental
Protection Agency.
Office of Air and water programs Publication Number APTD - 1357

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ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
TABLE OF CONTENTS
       Page
  PREFACE    ~
 1. INTRODUCTION    1
 '2. PROJECT SUMMARY   5
 3. TECHNICAL RESULTS  12
  3.1 Pumping Requirements  12
  3.2 variable Speed Drives  15
  3.3 Pumps    17
  3.4 variable Displacement Pumps 20
  3.5 pump/Drive Approaches  22
  3.6 Materials   40
r:  3.7 Test Programs  44
J  
  3.8 Conclusions   63
 4. INSTALLATION STUDIES  70
APPENDIX A
APPENDIX B
APPENDIX C
APPENDIX D
APPENDIX E
APPENDIX F
APPENDIX G
APPENDIX H
APPENDIX I
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operation of Differential/VSD Combination
TECO Seal Compatibility Tests
Gear Pump Design
vane Pump Design
Inducer Designs
variable Displacement vane Pump
Cycle Fluid properties and Comparisons
piston Pumps
Two-Stage Pumping

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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
PREFACE
This is the final report submitted by Chandler Evans
under the terms of Contract Number 68-01-0430, issued
by the Environmental Protection Agency of the united
States Government.
As specified in Exhibit A of the contract, Chandler
Evans was to conduct comprehensive design studies pur-
suant to the selection of conceptual models of vapor
generator feed pumps that will satisfy the performance
requirements of each of three Rankine cycle automotive
power systems currently under development.
In pursuing the objective of providing variable output
pumps for these applications, Chandler Evans conducted
investigations of two selected courses toward achieving
this goal:
1.
Fixed displacement pumps with variable
speed drives.
2.
variable displacement pumps.
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E:\G. H EPORT :\0.
APTD-1357
D.-\TE December 5, 1972
1.
INTRODUCTION
The Environmental Protection Agency is working with
three companies toward the development of Rankine cycle
engines for automotive applications.
As summarized
below, each of these companies is exploring a different
Rankine cycle concept utilizing a different cycle fluid.
Company
Cycle Fluid
Cycle Concept
Aerojet Liquid
Rocket company
sacramento
california
AEF-78
Turbine
Expander
steam Engine
watertown
Massachusetts
Systems
water
Reciprocating
Expander
Thermo Electron
corporation
waltham
Massachusetts
Fluorinol 85
Reciprocating
Expander
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E;\G. REPORT NO. -
APTD-1357
DATE December 5. 1972
In all cases, a pump is required within the cycle loop
to deliver working fluid from the condenser sump to the
high pressure boiler.
These pumps (called boiler feed
pumps) deliver working fluid ai pressures from 600 to
1200 psi over very wide flow and speed ranges.
A typical flow-speed operating envelope is illustrated
below:
OJ
4J
ra
~

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o
~
~
f
o
'7:J
r:
~
~
~
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.......",. ""',,,,- ,
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,'" '. eyc Ie ", "" "'. "" ".
, '" ' " '\.., " " "
, '", ....... Operating . "', '"'' "'-, "'" .

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"" "" ,.,~ . . , ". ". "-" "-"
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" "",,~ " "',."", ',," o.o"":/"C\
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, " '. ' . ). "'"
. '. ".', " ~\}.\.\.
speed
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E\"G. I~ EI'ORT \"0.
APTD-1357
DATE December 5, 1972
1.
INTRODUCTION
The Environmental Protection Agency is working with
three companies toward the development of Rankine cycle
engines for automotive applications.
As summarized
below, each of these companies is exploring a different
Rankine cycle concept utilizing a different cycle fluid.
company
Cycle Fluid
Cycle Concept
Aerojet Liquid
Rocket company
sacramento
california
AEF-78
Turbine
Expander
Steam Engine Systems
watertown
Massachusetts
Water
Reciprocating
Expander
Thermo Electron
corporation
waltham
Massachusetts
Fluorinol 85
Reciprocating
Expander
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~
ENG. REPOKT NO. -
APTD-1357
DATE December 5. 1972
In all cases, a pump is required within the cycle loop
to deliver working fluid from the condenser sump to the
high pressure boiler.
These pumps (called boiler feed
pumps) deliver working fluid at pressures from 600 to
1200 psi over very wide flow and speed ranges. '
A typical flow-speed operating envelope is illustrated
below:
Q)
.jJ
to
p::;

~
o
~
r:..
f
o " .
'7::J ."', , '-., '. . ", "" '
r:: . " ". "... " '-', " '... "
!:! ... "', "'. "... '''-.. .~...., ""," "'.
..J '\. ' '. " "-.. '. "'" .
N , '" "-.. "'" "'" "" "'" "'",
" "" '-',,- '-, " ""-, """ '" '"
.s2 ."., '. ", '............ '
'G ''''- " "-.. " ", " ", "
" " "', " '" ' -',
"" " " " "', ... .
"'" ' , Cycle' " ", " "
'" ,,'" ''''''''' "'-. ", " '-,
, """, "~"'. ope, rating """,'''-..,. ", ',,",., ,.

". ". Enve lope ", '. ", " '-.,
-; '" ","'" '" "'"

"~~'~"'-~,. '", '",,' "~~"'-:<""',;",",:,'

"'" ,', "', "'" " ' , '
. ,,,'" ,".,"',
'" "",- " ' " '" "'.
'" "'" ", '" '" "" "" co..,;!{\.
'''''' "'", '" " f'(\').:~{\.
" " . '\}..}.
. " f'l>).
speed
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ENG. UEPOkT NO. -
APTD-1357
DATE December 5, 1972
The principal pumping problem associated with the re-
quirements of this application is in maintaining high
efficiencies while delivering at all points within the
operating envelope.
A positive displacement pump is
considered the prime choice because of its inherent
relatively high efficiency.
A typical positive dis-
placement pump has a straight-line flow-speed relation-
ship.
The "no turndown" line in the preceding figure
represents a positive displacement pump sized to meet
the overall requirement of the operating envelope shown.
The excess flow must, however, be bypassed as cycle
demand varies within the envelope.
At "full turndown"
as noted on the figure, for instance, we can have turn-
downs of over 25:1.
Thus, a fixed displacement pump
must bypa&s more than 96% of its output at high pressure
to meet the extreme lower corner of the envelope.
It
is apparent, then, that a fixed displacement pump, using
a high pressure relief valve to obtain partial flows,
will result in inefficient operation.
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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
The next logical step would be to utilize a positive
displacement pump with a variable,output.
This can be
done in either of two ways.
First, by building a
mechanism within the pump, the displacement can be
varied at any engine speed.
Secondly, a fixed dis-
placement pump can be driven by a speed variator to
obtain the wide range of flows through pump speed
variation.
Again, referring to the preceding figure,
the output curve could be rotated from "no turndown"
to "full turndown" by varying the input drive speed
over the turndown range of 25:1 or whatever the require-
ment may be.
All pump output at high pressure would
then go to the boiler, eliminating the need for a bypass
valve to achieve the low flows.
This study considers the various options for accomplish-
ing the above noted function.
Since the requirements
of each of the power plants vary substantially, three
separate pumping systems have been studied in order to
provide the best overall approach for each application.
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ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
2.
PROJECT SUMMARY
In the conduct of the parallel program of investigating
fixed displacement pumps with variable speed drives and
variable displacement pumps, and through contacts with
the engine contr9ctors, the following conclusions and
positions have been formulated.
2.1
System Considerations
2. L 1
Looking at the general overall operating
envelopes of flow and speed for the various
boiler feed pumps, the specified turndown
ratios approach levels of 26:1.
2.1. 2
The data developed for the pumping systems
described herein were based on the current
published engine requirements.
There
appears to be a trend toward conservatism
in order to insure sufficient turndown
margin in the feed pumps.
with the
narrow-
ing of the requirements that can be expected
as the engine programs progress, the real
turndown levels should become less severe
and more easily obtainable.
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APTD-1357
DATE December 5, 1972
ENG. REPORT NO.
2.2
2.3
variable speed Drives
2.2.1
2.2.2
conventionally available designs for suit-
able variable speed drives produce speed
ratios in the ranges of 6:1 to 9:1.
These
may possibly be increased somewhat by ex-
tending the existing designs.
The high turndown ratios required by the
systems can be obtained by combining a
variable speed drive with a differential
to expand the available turndown ranges
of the drives, while paying a penalty in
power consumption, cost, size and weight.
positive Dis~lacement Pump
2.3.1
Gear and vane pumps are applicable devices
from th~ standpoints of technology and life
capability which have been developed over
the years on turbine fuels.
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'.
ENG. REPOI{T NO.
2.4
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2.3.2
2.3.3
",'. "
APTD-1357
DATE December 5, 1972
piston-type pumps have been developed and
are available for use in hydraulic fluids,
but their dependence on hydrodynamic con-
cepts for life and wear characteristics,
plus their inherently higher cost, place
them in a somewhat unfavorable position.
variable displacement vane pumps have proven
in practice their ability to handle low vis-
cosity fluids.
Cost and performance trade-
offs.will establish their rank in priority.
Vari~ble displacement piston pumps may
warrant consideration if some of the mech-
anical problems can be overcome.
System Approach
Based on the preceding points, our study points
toward a system with either a gear or vane type
pump in combination with a variable speed drive.
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ENG. REPORT NO.
APTD-1357
DATE
Decembe'r 5.. 1972
Furthermore, since the high flows are needed only
during acceleration transients and at very high
speed cruise conditions, a staged pump configu-
ration was investigated.
By this technique, the
basic pump characteristic follows a much lower
capacity limit through most of the operating range,
and only at the high demand condition will the
high capacity function be switched on.
By so doing,
the turndown range of the pump and variable speed
drive. can be narrowed for more efficient operation.
This may be accomplished by providing a supplemen-
tal pump to be called in on demand or by running a
two-stage pump in series normally, to be switched
to parallel operation on demand.
At the present
time, Chandler Evans favors the latter method.
This is described in more detail on page 26.
In keeping the pump-drive package within reasonable
performance limits, the expander low-speed, high
flow and high-speed, low flow corners of the oper-
ating envelope may become inaccessible.
In order
to achieve performance at these extremes, an accu-
mulator may be used at the high flow condition and
a bypass valve at low flow.
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. --. ,
APTD-1357
DATE
December 5, 1972
ENG. REPORT NO.
2.5
130015
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Pump Performance Assessment
Current performance predictions are based on avail-
able test data from Chandler Evans' and other manu-
facturers' pumps running with aviation gasolines
and kerosenes or their equivalent calibrating fluids.
Any real assessment of performance, including over-
all performance with the variable speed drive system,
must be determined from running these pumps on the
actual process fluids.
A Chandler Evans pump has been tested with Fluorinol
85, perchloroethylen~ (a substitute for AEF-78), and
AEF-78 in our Laboratory.
Additional testing of this
pump is planned with the AEF-78 fluid.
Gear and
bearing tests have been conducted to ascertain the
general wear characteristics of these components in
Fluorinol 85, AEF-78, perchloroethylene and water.
A variable displacement vane pump was delivered to
Aerojet Liquid Rocket Company to be run in their
test loop on AEF-78.
ALRC estimates that this
testing will commence on or about December 15, 1972.
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APTD-1357
December 5, 1972
ENG. REPORT NO.
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2.6
2.7
DATE
Engine Coordination
All of the engine contractors have been visited
and the results of our analytical studies and
design layouts conveyed to them.
Frequent commu-
nication has been maintained to coordinate our
efforts with their requirements.
program Direction
The development of any component in a system inti-
mately affects the entire system.
,
inte-'
I
Therefore,
gration of the feed pump into the power plant demands
investigation of the pump's effect on other components
and on the system in general.
No design should be considered as standing on its
own merits.
Before any pump design is accepted and
before any hardware is fabricated, the pump must be
satisfactorily coordinated into the whole system.
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ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
Chandler Evans submits that this can best be done
by the system contractor.
We, thus, recommend that
before hardware is fabricated, the pump supplier
and the engine contractor enter into a period of
active cooperation to develop the pump that best
fulfills the engine requirements.
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APTD-1357
December 5. 1972
ENG. REPORT NO.
DATE
3 .
"
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TECHNICAL RESULTS
3.1
Pumping Requirements
The pumping requirements for the three Rankine
cycle systems under study hav~ evolved to some
extent over the duration of this contract.
The
latest flow envelopes to which we addressed our
attention are illustrated in Figures 1, 2 and 3.
The Aerojet engine steady-state operating lines
for various road grades are superimposed on the
overall flow envelope (Figure 3).
Although this
information is not available for the other systems,
it is assumed that they will also follow a similar
pattern.
This type of information is very valuable
in understanding the feed pump's function in the
system and has enabled us to better work toward
satisfying the engine operating demands.
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ENG. REPORT NO. -
APTD-1357
DATE December 5, 1972
By applying the linear flow-speed relationship,
characteristic of positive displacement pumps at
constant pressure, to the corners of the per-
formance envelopes of Figures 1, 2 and 3, the
maximum turndown ratios for each system were cal-
culated to be:
TECO:
SES:
19.75
16.45
ALRC :
26
These turndown ratios were calculated by dividing
the slopes of the two straight lines through zero
which encompass the operating envelope.
,
(Referring
to the sketch on page 2, this is the slope of the
"No Turndown"
line divided by the slope of the
"Full Turndown" line.)
In actual practice, the turndowns.will be slightly
higher than shown because of volumetric losses,
which are primarily a function of pressure.
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ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
The specified performance parameters and other
pertinent data are listed in Table II.
To provide variable process fluid delivery over
the wide turndown ratios, two basic approaches
were studied:
1.
A fixed displacement pump on a
variable speed drive.
2.
variable displacement pump.
'\
In addition to these basic approaches, a fixed
displacement pump with bypassing was investigated
for the SES engine because its flow rates (and
power consumption) are so much lower than the
others.
The staging of a fixed displacement pump for series-
parallel operation was also examined for efficiency
optimization.
All of these concepts will be developed in the en-
suing pages and in the Appendices.
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APTD-1357
December 5. 1972
ENG. REPORT NO.
DATE
3.2
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variable speed Drives 
Table I lists several types of variable speed
drives and their salient features.
The torque
and efficiency characteristics of the currently
available types of variable speed drives are
illustrated in Figures 4 and 5.
The extremely wide turndown ranges needed by each
engine are beyond the limits of the finite-range
variable speed drives discovered in our market
research and analyzed in this study program.
By employing differentials in conjunction with

these drives, very high m~ltiplication in speed
I
ratios can be obtained; thus, extending their
ranges.
However, this is achieved at the expense
of increased power losses and increased unit size,
caused by a recirculating power loop within the
drive train.
The variable speed device must handle
this added load plus the torque transmitted to the
pump.
The net efficiency of the drive train is
thereby diminished.
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ENG. REPORT NO.
APTD-1357
December 5, 1972
DATE
The effect of employing a differential with a
variable speed drive is described analytically in
Appendix A of this report.
In the interest of minimizing complexity and cost,
and maximizing system efficiency, the combination
differential/variable speed drive is not recommended
unless there is no other recourse.
The necessary speed ranges could be obtained with
an infinitely variable speed variator.
static transmission is such a device.
The hydro-
However, it
was eliminated from consideration because of its
cost, size, complexity and poor efficiency.
The Lycoming Division of Aveo has an infinitely
variable planetary gear drive under development.
Its predicted performance characteristics are
attractive.
It was not considered in the analyses
contained herein because of its preliminary nature
a!ld the lack of solid definition.
In time, however,
it may prove to have application in a variable
delivery pumping system.
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APTD-l357
December 5, 1972
ENG. REPORT NO.
DATE
130015
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3.3
The input to the drive-ratio-varying device must
consider the specific requirement of the power
plant control system.
Ultimately, the position
change of a mechanism within the device determines
the output. This is usually accomplished by hy-
draulic pressure acting on a piston or piston/
spring combination.
The source of the pressure
and means for controlling it must be developed
into the power plant controlling mechanism by the
engine manufacturer.
Pumps
only a positive displacement pump can meet the
conditions of flow, pressure and efficiency de-
manded by the Rankine cycle automotive power plants.
The three basic types of positive displacement
pumps are described briefly below.
The role of
inducers in the pumping system is also mentioned.
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ENG. REPORT NO.
3.3.1
3.3.2
APTD-1357
DATE
December 5, 1972
Piston Pumps have the greatest potential
for high efficiencies, but need close
clearances to do so.
They are somewhat
intolerant of contaminant, tend to be
bulky and are expensive.
A discussion of
design considerations for piston pumps is
contained in Appendix H.
vane Pumps are simple but require some
precision in manufacturing.
They are of
moderate cost, tolerate contamination very
well and operate at reasonably good effi-
ciencies.
Descriptive data and design
considerations are contained in Appendix D.
Although several types of vane pumps were
investigated, only the balanced-rotor,
fixed-clearance type is presented in the
trade-off studies reported herein.
This
configuration offers the best efficiencies
because of its inherent low bearing and
rotor loading.
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ENG. REPORT NO.
3.3.3
3.3.4
APTD-1357
December 5, 1972
DATE
Gear Pumps are durable and simple.
They
have a reasonable tolerance for contami-
nation and are relatively inexpensive.
Gear pump efficiencies are within accept-
able levels for consideration in this
application, although they tend to be
lower than those of the piston and vane
pumps, especially at low speeds.
Descrip-
tive data and design considerations are
contained in Appendix c.
Inducers
The dry lift capabilities of Chandler Evans
gear and vane pumps are excellent.
There-
fore, no problems are anticipated at start-
up with the minimum liquid heads specified.
However, at operating speeds, the high pres-
sure element of each pump studied must be
charged to avoid cavitation.
Based on the
data contained in Table II, integrated
centrifugal inducers were designed for each
unit.
The development of the design data
is explained in Appendix E.
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APTD-1357
DATE
December 5, 1972
ENG. REPORT NO.
130015
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3.4
TO substantiate the analytical computations,
a Chandler Evans Model MFP-150 pump was run
at suppressed inlet 'pressures.
The test
results shown in Figure 36 indicate that
the inducer designs are conservative.
A jet inducer was included in the study of
Appendix E for possible application to a
bypassing approach for the SES system.
A
satisfactory inducer of the types shown in
Appendix E will preclude the need for any
other boost pump in the system.
variable Displacement Pumps
Both piston and vane pumps can readily be adapted
to variable displacement operation.
Such action
necessarily will add cost to the pump.
Chandler
Evans currently has a variable displacement vane
pump operating successfully on a development air-
craft.
Our experience with this pump is reflected
in the descriptive information of Appendix F.
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ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
commercially available variable displacement piston
pumps have been considered.
Prime producers of
these devices include Vickers and Sundstrand.
Meetings with engineers from these Companies and
discussions relating to the use of variable dis-
placement piston pumps with the Rankine cycle
fluids, have been discouraging at best.
These
pumps have been developed to operate with specific
hydraulic oils and use the fluid properties to
maximize performance.
They are dependent on hydro-
dynamic bearings to minimize friction, and require
viscosity/clearance combinations to diminish 1eak-
age.
Any variable displacement piston pump for
use with cycle fluids as they are now known will
require an extensive development effort.
The above mentioned Chandler Evans pump has been
sent to Aerojet for evaluation with the AEF-78
process fluid.
Any consideration of developing this type of pump
must be preceded by a thorough analysis of the test
results.
The performance and cost aspects must be
carefully studied, compared and traded off with
respect to the same aspects of the variable speed
drive.
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APTD-1357
DATE December 5, 1972
ENG. REPORT NO.
3.5
130015 .
REV. 1/65
Pump/Drive Approaches
In our effort to develop feed pump systems suitable
for the Rankine cycle automotive power plants under
study, our attention was primarily focused on per-
formance, especially as reflected in efficiency.
However, we were ever cognizant of the need to com-

pete in a large consumer market where both reli-
ability and cost are significant factors.
The basic performance requirements to which we
addressed ourselves are summarized in Table II.
The flow-speed relationships are illustrated in
Figures 1, 2 and 3.
inputs.
These items reflect our latest
Layout studies were made concurrent with the ana-
lytical investigations.
These are discussed in a
latter section of the report.
The specific approaches for each system are sum-
marized below.
All efficiency curves shown for the
gear and vane pumps presented herein include the
efficiencies of the inducers integrated into each
system.
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ENG. REPORT NO.
3.5.1
APTD-1357
DATE December 5. 1972
organic Fluid Reciprocator - TECO
Five distinct variable delivery pump arrange-
ments were analyzed for the TECO engine.
3.5.1.1
Fixed Displacement Gear pump on a
variable Speed Drive
A gear pump was investigated because
of its essential ruggedness and low
cost.
The particular gear pump ana-
lyzed here has a displacement of
0.66 cubic inches per revolution
(CIPR) .
The plot of Figure 6 is especially
descriptive of the operating param-
eters of a pump on a variable speed
drive.
The engine requirements are
shown in the upper right-hand quad-
rant.
The pump characteristic
appears in the upper left-hand
quadrant.
The lower right-hand
quadrant contains the fixed speed
ratio line of the expander gearbox.
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ENG. REPORT NO.
130015
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APTD-1357
DATE December 5, 1972
3.5.1.2
The lower left-hand quadrant shows
the pump speed envelope resulting
from the operation of a 9:1 ball-
type variable speed drive on drive
pad speed to obtain the desired
flows.
As indicated in Figure 7, the pump-
drive overall efficiency falls
short of meeting most of the speci-
fication limit points, although it
does approach them.
'"'
Fixed Displacement vane Pump on a
variable Speed Drive
Figures 8 and 9 show the effect of
(
a 0.6 CIPR vane pump in the system.
Although the peak efficiency of the
vane pump chosen for this appli-
cation is about the same as that
for the previously described gear
pump, its better off-design char-
acteristics bring it closer to
meeting the full range of specifi-
cation limits.
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\30015
REV. 1/65
APTD-1357
December 5, 1972
DATE
The spool-type variable speed drive
was selected to further enhance
efficiency.
(See Table I.)
How-
ever, this drive is unable to re-
duce pump speed sufficiently to
pick up the low flow points, as
illustrated in Figure 8.
Therefore,
a bypassing relief valve must be
employed to permit the necessary
flow reduction at these conditions.
The sharp drop off in efficiency
seen in Figure 9 on the 1800 rpm
line is a result of this bypassing
action.
Since relief valves are common to
all of our positive displacement
pumps for protection, the inclusion
of the bypassing function to ful-
fill the complete performance en-
velope does not add hardware to
the system.
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130015
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Et\G. REPORT NO.
APTD-1357
DATE
December 5, 1972
3.5.1.3
Two-Stage vane Pump on a Variable
Speed Drive
TO better utilize the full-range
efficiency characteristics of the
pump, a two-stage arrangement was
devised operating on the spool-
type variable speed drive.
The
schematic of Figure 10 illustrates
the basic function of this concept.
At low demand, the discharge of
one stage is fed to the inlet of
the other, splitting the pressure
rise between the two elements.
They are, thus, operating in series.
The displacement of each element in
this application is 0.3 CIPR.
When the demand exceeds the capa-
bility of this combination, both
elements go into parallel operation,
doubling the flow capacity.
The
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ENG. REPORT NO. -
130015
REV. 1/65
APTD-1357
December 5, 1972
DATE
speed-flow map of Figure 11 pro-
duces the improved efficiencies
shown in Figure 12.
The switching
point will be a function of pump
capacity, system considerations
and the nature of the control
. mechanism.
Referring to Figure 12, it can be
seen that the optimum switching
points are at the intersections of
the efficiency curves for series
and parallel operation at each
speed.
In this case, the flow-
speed relationship at optimum
switching is linear.
This suggests
the suitability of a simple speed
actuator.
Deadband must be built
into the device to avoid oscillation
at the switching point.
For more descriptive information
about two-stage pump operation,
refer to Appendix I.
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ENG. REPOI
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ENG. REPORT NO.
3.5.2
130015
REV. 1/65
APTD-1357
DATE
December 5. 1972
3.5.1.5
variable Displacement piston Pump
Since TECO currently has a develop-
ment program underway for a vari-
able displacement piston pump, we
have plotted their published effi-
ciencies in Figure 14 for comparison
purposes.
The power losses of the
TECO condenser-mounted boost pump
were neglected in determining these
efficiencies.
water Reciprocator - SES
Based on our past experience, vane pumps
only were considered for the SES engine
because of the material limitations imposed
by using water.
Furthermore, because of the lower power
demand of the feed pump in the SES system,
other than variable delivery pumps are among
the five concepts discussed below.
Many of the statements made in the section
on TECO pumps (3.5.1) apply here also.
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ENG. REPORT NO.
130015
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APTD-1357
DATE
December 5. 1972
3.5;2.1
Fixed Displacement vane Pump on a
variable Speed Drive
This arrangement utilizes the more
efficient but smaller turndown
spool-type variable speed drive.
As can be seen in the flow-speed
map of Figure 15, the high-speed
low-flow corner of the engine re-
quirement is unattainable by the
pump-drive combination.
Employment
of a bypass valve, however, will
permit operation in this region.
Because of the small size (0.25
CIPR) of this pump and the low
speed at which it runs, the volu-
metric and mechanical losses, which
are not proportional to size, be-
come a greater factor in the overall
efficiency, as exhibited in the
curves of Figure 16.
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ENG. REPORT NO.
130015
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APTD-1357
DATE
December 5. 1972
3.5.2.2
variable Displacement vane Pump
The efficiencies attainable with a
variable displacement vane pump in
the SES system are shown in Figure
17.
The best efficiencies of a variable
displacement vane pump occur at the
higher relative displacements.
Bal-
ancing the pump size against the
low capacity requirements of this
application necessarily entails slow
pump speeds, which further tends to
reduce the overall efficiency.
A
0.47 CIPR maximum displacement pump
was selected with a 1.5 speed in-
crease in the engine gearbox.
The
best efficiencies obtainable were
still generally low.
It does not seem that the SES sys-
tem warrants selection of such
complex equipment.
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ENG. REPORT NO.
130015
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APTD-1357
DATE
December 5. 1972
3.5.2.3
3.5.2.4
Fixed Displacement vane Pump with
Bypass
The low feed pump capacity required
by theSES system justifies ex-
ploration of a fixed displacement
pump without speed or displacement
variation.
Figure 18 depicts the
power curves for a simple bypassing
vane pump of 0.47 CIPR displacement.
Although efficiency suffers from
the lost work of bypassing, the
actual power loss is quite low (less
than 5 horsepower at the worst con-
dition) .
For this reason and be-
cause of the simplicity of this
method, the system may well be able
to tolerate such a power loss.
Two-Stage vane Pump with Bypass
TO reduce the losses in a bypassing
system, the pump may be staged in a
manner similar to that shown in
Figure 10.
At the low speed, high
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ENG. REPORT NO.
130015
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APTD-1357
December 5, 1972
DATE
flow points, the two elements will
be operating in parallel to meet
the engine demand.
As engine speed
increases,
output from the direct-
driven pump far exceeds require-
ments.
At some appropriate signal,
a valve can be actuated which will
direct the discharge of one element
to the inlet of the other;
thus,
putting both elements in series
operation.
Half of the full pressure rise of
the system will be carried by each
The maximum power loss is
stage.
I
thus diminished by 2~1o in this
arrangement, where the displacement
of each stage is 0.44 CIPR with
the pump running at expander speed.
The power curves for this pump are
shown in Figure 19.
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ENG. REPORT NO. -
APTD-1357
DATE
December 5, 1972
3.5.2.5
The switching point will be a func-
tion of pump capacity, system con-
siderations and the nature of the
control mechanism.
However, it is
suggested that consideration be
given to a simple differential flow
sensor that will switch the pump
from the parallel to the series
mode when bypass flow exceeds en-
gine demand flow.
Fixed Displacement vane Pump with
Inducer Bypass
Another unique method of reducing
the losses in a bypassing system is
the recovery of some of the lost
energy in a jet inducer.
The by-
pass function can be performed
within the inducer by using a
pintle nozzle.
This concept is
developed on page E-7 of Appendix
E.
The power curves for this
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REV. 1165
ENG. REPORT NO.
3.5.3
APTD-1357
December 5, 1972
DATE
arrangement are shown in Figure 20
as a function of flow.
Figure 21
shows a comparison of the power re-
quirements of this method, with
respect to those of the simple by-
passing pump discussed above
(3.5.2.3).
Both pumps are the same size and are
running at the same speeds.
organic Fluid Turbine - ALRC
The high flow rates of the ALRC system place
more of a burden on the feed pump to minimize
losses.
The gear and vane pump concepts which have
been studied are presented below.
3.5.3.1
Fixed Displacement Gear pump on a
variable Speed Drive
As seen in the performance envelope
of Figure 22, a 0.9 cubic inch per
revolution (CIPR) gear pump on a
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ENG. REPORT NO.
130015
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APTD-1357
DATE
December 5, 1972
3.5.3.2
ball-type variable speed drive,
having a 9:1 speed ratio range, is,
by itself, unable to fulfill the
complete engine flow envelope be-
cause of the extremely high turn-
down required.
An accumulator can
accommodate the transients which
occur in the low-speed high-flow
corner.
The efficiencies accruing
to this configuration fail to meet
specification limits as indicated
in Figure 23.
Fixed Displacement vane Pump on a
variable Speed Drive
A vane pump of the same size as
above on the same variable speed
drive exhibits better efficiencies
over the full flow range (see
Figure 25) because of its inherent
flatter efficiency characteristic.
(see Appendices C and D.)
In
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ENG. REPORT NO.
130015
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APTD-1357
DATE December 5, 1972
3.5.3.3
Figure 24, it is noted that the
gearbox ratio must be adjusted
slightly to bring in some of the
low-flow points which had fallen
out of the range of the variable
speed drive because of the better
vane pump volumetric efficiency at
low speed.
Two-stage Gear Pump on a variable
Speed Drive
To better utilize the full range
efficiency capability of the gear
pump, a two-stage series-parallel
arrangement was explored.
The
arrangement will be similar to that
shown in Figure 10 and its function
will be essentially as described in
Section 3.5.1.3.
The displacement
of each element will be 0.6 CIPR.
This configuration also permitted
the use of the lower turndown,
higher efficiency, spool-type
variable speed drive.
However, as
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ENG. REPORT NO.
130015
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APTD-1357
DATE
December 5, .1972
3.5.3.4
indicated in Figure 26, the extreme
corners of the flow envelope are
still inaccessible.
This can be
solved by using an accumulator at
high flow and a dump valve at low
flow.
A substantial improvement in effi-
ciency is noted from Figures 27 and
28.
The switching point is impor-
tant in maintaining high efficiencies
at all conditions.
Two-stage vane pump on a variable
Speed Drive
A further improvement in full range
efficiency can be obtained by using
a vane pump in a series-parallel
arrangement.
This pump also com-
prises two 0.6 CIPR elements.
As
observed in Figure 29, the unattain-
able low-speed high-flow corner of
the flow envelope is so minimal that
it probably can be neglected.
A
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ENG. REPORT NO.
130015
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DATE
December 5, 1972
APTD-1357
3.5.3.5
dump valve can be used at the low
flow points.
Efficiencies are shown
in Figures 30 and 31.
variable Displacement vane Pump
The efficiencies accruing to a
variable displacement vane pump in
the ALRC system are shown in Figures
32 and 33.
The maximum displacement
of this pump is 1.1 CIPR.
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APTD-1357
December 5, 1972
ENG. REPORT NO.
3.6
DATE
Materials
The materials utilized in the construction of the
various vapor generator feed pumps have been select-
ed on their ability to perform adequately in the
specific working fluids.
The selections were based
on material compatibility data received from the
producers and users of Fluorinol 85 and AEF-78, as
well as on tests run by Chandler Evans.
Main housings will be constructed from cast 356
aluminum or gray cast iron.
For the water feed
pump, only cast 356 aluminum will be considered.
Anodizing will be used to provide additional corro-
sion resistance for the cast aluminum.
Impellers will be constructed from cast 356 alumi-
num and, as in the case of the aluminum housings,
will be anodized to afford additional corrosion
protection.
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ENG. REPORT NO.
APTD-1357
DATE
December 5. 1972
Pumping gears, with their associated drive trains,
will be manufactured from either nitrided AMS 6470
(used extensively in Chandler Evans fuel pumps) or
from carburized SAE 8620.
The drive splines will
be chromium plated to provide additional wear
resistance.
In the case of the vane pump working
on water, the drive shaft will be fabricated from
Greek Ascoloy, a corrosion resistant steel.
AISI420 stainless steel, hardened to Rockwell C
48-53, and AISI 52100 steel, hardened to Rockwell
C 60, have been selected as candidate materials
for vane pump rotors.
The former alloy will pro-
vide the necessary corrosion resistance foroper-
ation in the water environment.
An air hardening
tool steel has also been considered as a rotor
material for the organic fluid feed pump.
..
carbon-graphite, tool steel and Stellite are con-
sidered prime candidates for vanes.
In the case
oi the carbon graphite, a special grade has been
selected with a coefficient of expansion that
. 130015
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130015
REV. '/65
ENG. REPOkT NO.
APTD-1357
December 5, 1972
DATE
matches that of the rotor to minimize fluid losses
at elevated temperatures.
This problem will not
exist in the case of the tool steel and stellite
vanes.
Tool steel is not recommended for the
water system because of its lack of corrosion
.resistance.
other materials that might be con-
sidered for vanes are S-monel and glass-filled
polyimide (for the water system).
440C Stainless steel and 52100 steel have been
selected as liner materials for the vane pumps.
The 440C will be hardened to Rockwell C 53-60,
and the 52100 steel to Rockwell C 60. 52100 has
been eliminated as a liner material for the water
feed pump because of its lack of corrosion resis-
tance.
Rotational wear tests have been conducted on a
carbon graphite/440C stainless steel system to
ascertain the suitability of this combination for
use as vane and liner, respectively.
The results
are detailed under Bearing Material Tests, page 55.
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ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
In the gear and vane pumps presented in this report,
the pumping element bearings are lubricated by the
working fluid.
only resin impregnated carbon
graphite is recommended for these bearings in both
the Fluorinol 85 and water.
This material may also
be used in the AEF-78 in addition to leaded bronze.
As demonstrated by Chandler Evans testing, each set
of materials and fluids has a critical load-speed
limit.
Bearing designs will be based on this
information.
The selection of suitable seal materials has re-
quired careful consideration and because of the
variety of fluids involved, the materials utilized
for one fluid may be unsatisfactory for another.
Ethylene propylene rubber is recommended for use
in Fluorinol 85 and FC75, viton (fluorocarbon)
for use in perchloroethylene, neoprene for use in
AEF-78 and nitrile for use in water.
Tables III and IV summarize the material selection
for vane pumps and gear pumps, respectively.
130015
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APTD-1357
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DATE
ENG. REPORT NO.
130015
REV. 1/65
3.7
Appendix G provides data on the physical properties
of the loop fluids in comparison with the proper-
ties of CECa used fuels and other similar fluids.
Test programs
3.7.1
Micro-Ryder Testing of Nitrided and carburized
Steel Gears
Pumping gear evaluations for gear loading
capacity and gear life have been conducted
with water, Fluorinol 85 and AEF-78, and
compared with JP-4 using AMS 6260 gears.
The tests were carried out with the Micro-
Ryder gear machine which is run at a con-
stant speed and gear geometry while varying
the gear loading torque in incremental steps.
Base line running was conducted on nitrided
AMS 6470 gears in MIL-J-5624, JP-4 aviation
fuel, since voluminous service history in-
formation is available on this combination.
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130015
REV. '165
- --- ----L_----~-_._-
ENG. REPORT NO.
APTD-1357
December 5, 1972
DATE
A standard gear material, carburized AMS
6260, was utilized to evaluate the relative
scoring and wear resistance of the various
system fluids.
The relative scoring is shown in Figure 34
which shows percent of tooth area scuffed
versus machine load.
A lower amount of
scuffing indicates that a higher gear tooth
load is possible for a given life require-
ment.
The maximum scoring factors (pressure x
velocity x Length, PVT) for gear pump design,
using typical pump gear materials, are known.
Figure 34 indicates that both FL-85 and AEF-
78 are good fluids for gear pump applications.
On the other hand, we see that water is not
as readily adaptable.
using limiting PVT factors for the various
gear materials selected, a series of gear
pump parameters can be established, biased
by the scuff resistance of the fluid used,
as determined by such testing reported herein.
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130015
REV. 1{65
ENG. REPORT NO.
3.7.2
3.7.3
APTD-1357 '
December 5, 1972
DATE
Elastomer Testing at TECO in Fluorinol 85
samples of both fluorosilicone and silicon
rubber seals were sent to TECO for their
test and evaluation in Fluorinol 85.
Their
test report is included as Appendix B of
this report.
Elastomer Testing at ALRC in AEF-78
samples of both fluorosilicone and silicone
compounds were sent to ALRC for their test
and evaluation in AEF-78.
These seal materials were placed in a con-
tainer of AEF-78 at ambient temperature.
Air
was evacuated from the container preparatory
to raising the temperature.
However, the
seals began to deteriorate immediately as
indicated by discoloration of the fluid.
The test was halted, since it was obvious
that AEF-78 is a solvent for fluorosilicone
and silicone.
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3.7.4
1300\5
REV. 1/65
APTD-1357
DATE
December 5, 1972
Pump Testinq
3.7.4.1
Gear Pump
A Chandler Evans Model MFP-150 Main
Fuel Pump was tested on MIL-T-5624
JP-4, isooctane, Fluorinol 85 and
and perchloroethylene (a recommended
substitute for AEF-78).
Since the
MFP-150 has a history of pumping
JP-4 and isooctane, the testing with
these aviation fuels was used as a
basis of comparison for the other
fluids.
Referring to the fluid property data
contained in Appendix G, wherein the
process fluid viscosities were equal
to or greater than the aviation fuel
viscosities, it was expected that
the volumetric performance with the
process fluids would be at least as
good as the performance with the
aviation fuels.
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130015
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APTD-1357
December 5J 1972
DATE
The volumetric performance noted
during the pump's operation on
Fluorinol 85 at low speeds and pres-
sures at the beginning of the test
cycle was as good as or better than
the prior calibration on MIL-J-5624J
Grade JP-4.
The pump performance
did not deteriorate significantly
until later in the cycle during the
highest discharge pressures and pump
speeds.
Subsequent running with
perchloroethylene showed a pronounced
decrease in the overall efficiency
due mainly to a loss of mechanical
efficiency.
See Figure 35.
The detail parts inspection after
test revealed severe pumping gear
bearing face wear with moderate
journal bearing wear.
These obser-
vations tend to support the pump's
performance loss due to mechanical
efficiency degradation.
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130015
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APTD-1357
December 5, 1972
DATE
The gear tooth flanks remained in
good condition while running on the
Fluorinol 85, which further confirmed
the Micro-Ryder gear test results
reported on page 44.
The gear tooth flanks were badly
scuffed after running on perchloro-
ethylene, which points to the poor
lubricity characteristics of this
fluid.
Since lubricity is a function
of chemical composition, and per-
chloroethylenediffers chemically
from AEF-78, an accurate assessment
of a gear pump in AEF-78 will require
a test in that fluid.
The test pump was fitted with new
pumping gears and bearings and was
returned to test to evaluate the NPSH
(net positive suction head) charac-
teristics of the impeller boost stage
in Fluorinol 85.
The impeller per-
formance is shown on Figure 36.
The
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130015
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APTD-1357
December 5, 1972
DATE
test data indicates that the state-
of-the-art designs will adequately
fulfill the requirements of each of
the Rankine Cycle Systems.
As far as the Fluorinol 85 is con-
cerned, the problem in defining a
gear pump to handle this fluid
resolves to the development of
suitable bearings.
This appraisal also applies to the
perchloroethylene, plus the need
for selection of a gear material
and geometry to overcome the tooth
scuffing.
The Chandler Evans MFP-150 pump
which has been used as a "base line"
for evaluating gear pumps in both
the TECD and ALRC systems was designed
for operation over a pressure range of
200 to 860 psi.
since, in these Rankine
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ENG. REPORT NO.
130015
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APTD-1357
December 5. 1972
DATE
cycle applications, the pressures
are maintained at consistently higher
levels for all operating conditions,
the area under pressure loading can
be reduced substantially while still
assuring adequate gear face sealing.
Thus, it is estimated that the gear
thrust loading which appears to be
the major obstacle in running the
MFP-150 pump in Fluorinol 85 and
perchloroethylene can probably be
decreased by a factor in the order
of 2 to 1.
Another approach to
alleviating thrust overload would
be employment of a fixed-clearance
gear package.
In the matter of radial loads, which
do not seem to be as severe as the
thrust loads, the journal can be
enlarged in accordance with the
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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
criterion stated on page C-6 of
Appendix C.
The diameter of the
journal bearing can safely be in-
creased by ~/o with a consequent
radial load reduction of 8%.
The use of helical pumping gears
will further reduce radial loading,
as well as providing more tooth
contact which will tend to prevent
the scuffing observed from pumping
perchloroethylene.
The Model MPP-150 pump used in the
testing described above was fitted
out with carbon-graphite pumping
gear bearings for a preliminary
evaluation of performance on
pluorinol 85 and AEP-78.
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130015
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ENG. REPORT NO.
APTD-1357
December 5, 1972
DATE
The efficiencies shown in Figure 37
are comparable to those obtained
from operating this pump on JP-4
aviation fuel.
It should be pointed
out, however, that in the several
tests and rebuilds to which this
pump had been subjected, the effi-
ciencies would be expected to suffer.
The data plotted in Figure 37
is in
the normally low-efficiency range
of this particular pump.
Of interest
is the improvement of overall effi-
ciency with running on AEF-78.
The use of carbon graphite will
dictate certain design practices,
such as no sharp corners and no thin
sections.
However, to expedite this
testing in an existing pump, the
carbon bearings were fabricated to
the same configuration as the bronze
bearings for which the pump was
originally designed.
During the
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!
130015
REV. 1/65
APTD-1357
DATE
December 5, 1972
3.7.4.2
testing one of the pressure loaded
bearings fractured at a sharp
corner.
In spite of this failureJ
no significant wear was exhibited
on either the thrust or journal
bearing surfaces.
The results of this testing en-
courages us to feel that carbon
bearings can be readily adapted
to this application.
variable Displacement vane Pump
A variable displacement vane pump
was delivered to Aerojet Liquid
Rocket Company to be run in their
test loop on AEP-78.
ALRC esti-
mates that this testing will
commence on or about December 15J
1972.
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ENG. REPORT NO.
3.7.5
APTD-1357
December 5. 1972
DATE
These tests, in addition to deter-
mining the adaptability of this
pump to the Aerojet system, will
provide a comparison of performance
in AEF-78 with respect to aviation
fuel.
Bearing Material Tests
A series of bearing wear tests were conducted
on several candidate bearing materials in each
of the working fluids.
The results of these
tests are intended to set load-speed envelopes
for both bearing and vane design purposes.
The tests were performed on Chandler Evans'
wear test rig in which a rotating upper speci-
men is loaded against a fixed lower specimen,
with both specimens immersed in a bath of the
working fluid.
Both the load and the speed
The tests, which lasted for
are variable.
periods of 30-45 minutes, were run at room
temperature, but during the test, the fluid
temperature rose, in some cases exceeding
120°F.
The results of these tests are
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ENG. REPORT NO.
130015
REV. 1165
APTD-1357
December 5, 1972
DATE
summarized below.
Fluorinol 85
(a) Leaded Bronze vs. Nitrided Nitralloy
Lower Specimen - 2~1o leaded bronze and
Electrofilm solid film
lubricant
upper Specimen -
Nitrided Nitralloy
(AMS 6470)
case Depth - .012" Min.
Hardness - Rockwell l5N,
92 Min.
Duration of Test - 45 Minutes
Testing on this combination was restricted
to one test at 135 PSI load and 1550 fpm,
producing a PV of 209,250.
Examination
of the wear surfaces showed no signs of
distress.
Further testing of this system
was abandoned when it was discovered that
Fluorinol 85 had an adverse reaction with
the leaded bronze (see page 61).
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ENG. REPORT NO.
130015
REV. 1165
APTD-1357
December 5, 1972
DATE
(b) Resin Impregnated carbon Graphite vs.
Nitrided Nitralloy
Lower Specimen - Graphitar 39 (U. S.
Graphite)
upper Specimen -
Nitrided Nitralloy
(AMS 6470)
case Depth - .012" Min.
Hardness - Rockwell 15N,
92 Min.
Duration of Test - 30 Minutes
The test results indicate that the PV
should not exceed 930,000.
A load-speed
envelope is shown in Figure 38.
(c) Resin Impregnated carbon-Graphite vs.
440C Stainless Steel
Lower ~pecimen - 440C stainless
Hardness Rc 55

upper Specimen - Graphitar 113
Graphite)
Steel
(u. S.
Duration of Test - 45 Minutes
The test results indicate a maximum
allowable pv of 570,240.
A load-speed
envelope is shown in Figure 39.
-57-

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
December 5, 1972.
DATE
AEF-78
(a) Leaded Bronze vs. Nitrided Nitralloy
Lower Specimen - 20% Leaded Bronze and
Electrofilm solid film
lubricant
upper Specimen -
Nitrided Nitralloy
(AMS 6470)
case Depth - .012" Min.
Hardness - Rockwell l5N,
92 Min.
Duration of Test - 30 Minutes
The test results indicate an allowable
PV range in excess of 2,378,000.
Typical
sleeve bearing PV values encountered in
Chandler Evans pumps are usually well
below this value.
A load-speed envelope
is shown in Figure 40.
(b) Resin Impregnated carbon Graphite vs.
440C stainless steel
Lower Specimen
- 440C Stainless steel
Hardness Rc 55

~ Gr~phitar 113 (U. S.
Graphite)

Duration of Test - 30 Minutes
upper Specimen
-58-

-------
ENG. REPORT NO. -
APTD-1357
DATE
December 5. 1972
The test results indicate that the PV
should not exceed 570,240.
A load-speed
envelope is shown in Figure 41.
water (Distilled)
(a) Resin Impregnated Carbon Graphite vs.
440C Stainless Steel
Lower Specimen - 440C Stainless
Hardness - Rc 55

Upper Specimen - Graphitar 113 (U. S.
Graphite)
Duration of Test - 30 Minutes
The test results indicate an allowable
PV range up to at least 570,240.
A
load-speed envelope is shown in Figure 42.
130015
REV. 1/65
-59-

-------
ENG. REPORT NO.
130015
REV. 1{65
APTD-1357
December 5. 1972
DATE
Perchloroethylene
(a) Leaded Bronze vs. Nitrided Nitralloy
Lower Specimen - 20% Leaded Bronze and
Electrofilm solid film
lubricant
upper Specimen -
Nitrided Nitralloy
(AMS .6470)
case Depth - .012" Min.
Hardness - Rockwell 15N,
92 Min.
Duration of Test - 45 Minutes
The test results indicate an allowable
PV range up to at least 634,725.
A load-
speed envelope in shown in Figure 43.
(b) Resin Impregnated carbon Graphite vs.
440c Stainless Steel
Lower Specimen - 440C stainless Steel
Hardness Rc 55

upper Specimen - Graphitar 113 (U. S.
Graphite)

Duration of Test - 45 Minutes
-60-

-------
- ,.-- --
'.;: ,f ..' ~: ~
ENG. REPORT NO. -
APTD-1357
DATE
December 5, 1972
Only one test was performed on this
combination at a load of 510 PSI and a
speed of 2400 fpm, producing a PV of
1,224,000.
Discoloration of the 440C
track showed that this condition was
marginal.
No further tests were run on
this material system.
In commenting on allowable PV values for vane
tips, it is Chandler Evans experience that
calculated PVvalues using vane tip Hertz
loads can exceed those predicted by wear
test results by a substantial margin, without
any noticeable evidence of wear.
Testing of the MFP-150 pump, which showed
excessive bearing wear while running on
Fluorinol 85, also produced a discoloration
of the test fluid and prompted an investi-
gation into the effect of Fluorinol 85 on
leaded bronze.
Immersion tests were con-
ducted on samples of leaded bronze with and
130015
REV. 1/65
-61-

-------
El\G. REPORT ;\;0,
130015
REV. 1/65
APTD-1357
December 5, 1972
DATE
"
without the dry film lubricant in Fluorinol
85 at room temperature.
After 2-3 hours,
the fluid became milky and with continued
exposure, a heavy white precipitate was
observed.
Analysis of this precipitate
showed that it was rich in lead and it was
concluded that Fluorinol 85 was not com-
patible with alloys containing lead.
As a
result of these findings, Halocarbon, the
producers of Fluorinol 85, was informed and
additional work by Halocarbon confirmed
Chandler Evans test results.
Immersion tests of leaded bronze in AEF-78
at room temperature showed no reaction after
72 hours.
Immersion tests of resin impregnated carbon
graphite in boiling Fluorinol 85 also showed
no reaction after 48 hours.
-62-

-------
ENG. REPOkT NO.
3.8
130015
REV. 1/65
APTD-1357
December 5, 1972
DATE
Conclusions
3.8.1
3.8.2
variable Speed Drives
The variable displacement traction drives
included in the conceptual models developed
in this study are rugged, simple and reason-
ably efficient.
They deserve consideration
in a
variable delivery pumping system.
There is activity currently taking place in
th~s field toward increasing speed range and
efficiency.
Such advances will further en-
ha~ce the position of variable speed drives
in this application.
Pumps
3.8.2.1
General
None of the pumps analyzed in this
study, be they the conceptual models
developed by Chandler Evans or units
-63-

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
3.8.2.2
under development by the system
contractors, meets the full range
of efficiencies specified by this
contract (5~/o at l~/o flow and 7~/o
between 30% and 8~/o flow).
The
arrangement that will most nearly
fulfill specification limits is a
two-stage vane pump on a variable
speed drive.
Gear Pumps
Gear pumps will perform very re-
liably in both pluorinol 85 and
AEP-78.
carbon graphite bearings
will function satisfactorily in
both fluids, while leaded bronze
will also serve the AEP-78.
A gear pump is not recommended for
water.
-64-

-------
ENG. REPORT NO.
130015
REV. 1/65
APTD-1357
DATE
December 5. 1972
There are development activities
underway at Chandler Evans to im-
prove gear pump efficiencies, such
as the use of helical gears and
the employment of fixed clearances.
Success in these efforts may prove
gear pumps to be viable candidates
for the organic fluid Rankine cycle
feed pumps.
However,
the current generation of
gear pumps will not meet the effi-
ciency requirements specified in
this contract.
If gear pump efficiencies can be
raised to acceptable levels, they
would be an ideal pump for this
application because of their in-
herent ruggedness and low cost.
-65-

-------
130015
REV. 1/65
ENG. REPORT NO.
" -"~'I-
APTD-1357
DATE
December 5, 1972
3.8.2.3
3.8.2.4
vane Pumps
The vane pumps investigated in this
study will be run at sufficiently
low speeds to permit the use of low
density vane materials;
ducing operating losses.
thus re-
Although
not considered in the fixed displace-
ment vane pumps presented in this
report, a further improvement in
efficiency may be obtained by using
hydrodynamic vane tips.
The basic efficiency characteristics
of vane pumps recommend them for
prime consideration as Rankine cycle
feed pumps.
variable Displacement Pumps
The nature of the performance
enve-
lopes for these Rankine cycle feed
pumps is such that a variable dis-
placement pump must function in the
-66-

-------
ENG. REPORT 1\0.
3.8.3
130015
REV. '/65
APTD-l357
DATE . December 5, 1972
low percentage range of full dis-
placement at most of the operating
conditions.
Efficiencies are low
under these circumstances.
For
this reason and because of com-
plexity and cost, variable dis-
placement vane pumps are not
recommended.
The mechanical problems of sealing
the working fluid from the lubri-
cant coupled with the size of a
piston pump have led us to view
this type of pump unfavorably for
handling the low viscosity Rankine
cycle working fluids.
Specific Pumps and Drives
3.8.3.1
organic Fluid Reciprocator - TECO
\
The best efficiencies are obtained
by a two-stage vane pump on a
-67-

-------
130015
REV. 1/65
ENG. REPOKT NO.
APTD-1357
DATE
December 5, 1972
3.8.3.2
6.25:1 turndown variable speed
drive.
The low-flow efficiencies
are especially good.
However,
a simple vane pump on a
variable speed drive exhibits
reasonably good efficiencies and
may warrant consideration on the
basis of simplicity.
water Reciprocator - SES
The low capacity of the feed pump
in the water system with its con-
comitant low power demands does not
seem to justify investment
variable delivery pump.
in a
Therefore, a fixed displacement by-
passing pump is recommended.
The
simplest and most efficient over
the full operating range is a vane
pump bypassing through a jet in-
ducer with a pintle nozzle serving
as the bypass valve.
-68-

-------
ENG. REPORT NO.
3.8.4
130015
REV. 1/65
APTD-1357
DATE
December 5, 1972
We have limited our attention to
vane pumps because of material
restrictions.
3.8.3.3
organic Fluid Turbine - ALRC
A two-stage vane pump on a 6.25:1
turndown variable speed drive comes
close to meeting the specified
efficiency requirements at all
operating conditions.
Inducers
Inducers are needed by all of the pumps
presented herein.
They will be capable of
handling the expected net positive suction
heads (NPSH) at pump inlet.
-69-

-------
ENG. REPORT NO.
APTD-1357
DATE December 5 J 1972
4.
INSTALLATION STUDIES
Installation, size and envelope data have been prepared
for the various power plants under study based on the
available information at the time of preparation.
It
was noted during our contacts with the system contractors
that these power plants are, in general, going through
continual installation and envelope changes.
Although
the updated versions of our drawings will be to latest
known requirements of space and mounting, it is noted
that any future effort, after definition of concept,
must be more closely coordinated with and made a part
of any engine program where the results of this study
are applied.
we have tabulated below by Company, Drawing Number and
Description, the installation study effort to date.
Copies of these drawings have been transmitted to the
engine contractors and to the EPA.
The sallent pump features have been extracted from
several of these layouts and are included herein as
Figures 44 through 50.
These illustrations show the
130015
REV. 1/65
-70-

-------
ENG. REPORT NO.
APTD-1357
DATE
December 5. 1972
basic design concepts and give approximate envelope
dimensions.
Some modification of component arrangement
and space envelope is possible in these pumps to
accommodate engine requirements.
4.1
Thermo Electron corporation
L1640J2
Gear pump on sheave type variable speed
drive with differential - revised engine
drive housing.
L1640J3
Gear pump on sheave type variable speed
drive with differential - adapting to
existing engine drive housing.
L1640J5
Gear Pump on Sundstrand hydrostatic
variable speed drive.
L1640J6
Gear pump on TPI traction type variable
speed drive.
130015
REV. 1/65
-71-

-------
130015
REV. 1/65
ENG. REPORT NO.
4.2
L1640J7
L1640J8
L1640J9
APTD-1357
DATE December 5, 1972
Gear pump on TPI traction type variable
speed drive with differential.
Gear pump on TPI traction type variable
speed drive with differential sized for
added power requirement of differential.
Gear pump on Cleveland worm & Gear ball-
type variable speed drive.
L1640D10) variations of a two-stage fixed dis-
~~~:~~~;~ placement gear pump on a variable speed
drive.
steam Engine Systems
L1643A3
L1643J5
L1643D6
Cross section of 2.5 GPM vane pump.
vane pump on TPI traction type variable
speed drive with differential.
vane pump on TPI traction type variable
speed drive (no differential).
-72-

-------
ENG. REPORT NO.
130015
REV. 1/65
4.3
L1643D7
L1643D8
APTD-1357
December 5. 1972
DATE
vane pump sized to meet SES limiting
condition and bypass at other conditions.
Two-stage fixed displacement vane pump.
Aerojet Liquid Rocket Company
L1642Dl
L1642D2
L1642J3
L1642J4
L1642D5
variable displacement vane pump designed
for ALRC envelope.
variable displacement vane pump in bar
stock housing.
Layout showing installation features of
a variable displacement vane pump pre-
pared for delivery to ALRC.
Gear pump on TPI traction type variable
speed drive.
vane pump on TPI traction type variable
speed drive.
-73-

-------
130015
REV. 1/65
ENG. REPORT NO.
L1642D6
L1640J9
99l39X
APTD-1357
DATE December 5, 1972
Two-stage fixed displacement vane pump.
Gear pump on Cleveland Worm & Gear ball-
type variable speed drive.
Assembly drawing of variable displacement
vane pump supplied to ALRC for testing.
-74-

-------
TABLE I - VARIABLE SPEED DRIV :S
y~ SPEED
DRIVE TYPE ' RATIO
i RANGE
[ABLE PITCH SHEAVE
	 Fixed Speed Pulley
rfV5
nput - — 1| II ~- Control Mechanism
J t^n-
)utput £Jj Variable Speed Pulley
Pr
tOSTATIC
-.y^F -T
J sllteaL--. lyfe^!!^
ffL

xBR ^-^
Input \X lil 2/y Output
1:2.5
11
14 nt* H lirnill r 3 I
1:36
to
2.2:1
(8:1)
0:1
(Inf.)
1:2.5
to
2.5:1
(6.25:1)
1:3
to
3:1
(9:1)
EFFICIENCY
100— 	 	 	 - •


i)
e
• 95- 	
14
•
o. ..__., 80- 	 - 	
u 	 	 	
e 	 	 	 1
£ 0 0 5 1.0 1
M
Spaed Ratio -
Io6— 	 	 	

a
c
U qn --^•'••••ij;
« 	 C- 	
' :::::::::
i _.i
>• so—.:"' 	 	

C "~ "


O 7Q_ 	 	 	
%4
|g 0 0.5 1.0 1.!
Speed Ratio -
SIZE
12 H.P.






..,,« •'. 	 lo"x 23"
*' - - - - - ' x9 "








52025
)utput /Input

""•'"• " 	 PUMP

	 . _ 	 6"x 6"
	 x7"



gi;!!M!!!!!!::


	 MOTOR


it x 6"

Output/Input



!':; si ;;;;:::: x 10-

5 2.0 2.5
Output/Inpot




- 10" DIA.
*|^ 	 -. „
	 l^_ 	 	

^ fc
5 »




2.0 2.5
Output/Input
CONTROL
Dis-
place-
ment
Dis-

Force
Dis-
place-
ment
STATE
OF
DEV.
Avail-
able
Avail-
able
Proto-
type
Avail-
able
Design
to be
Modi-
fied
MANUFACTURERS
CONTACTED
Llewellen Mfg. Co.
Speed Selector, Inc.
Winsmith Division
UMC Industries
Gerbing Mfg. Co.
Reliance Electric Co.
i
Sunstrand
Division
Hydeco Division
General Signal Corp.
i
Traction Propulsion
Inc.
Cleveland Worm & Gear
Division Eaton Corp.

-------
INSTALLATION
Fluid
Expander Speed Range
Flow control
Pump and Elevation -
o Grade (1)
Pump and Elevation -
3 CJ>!o Grade (1)
Minimum Liquid Head at Inlet
Mounting
coupling

Rotation (Pump viewed
from Shaft End)
Expander to Pump Drive
Ratio
Inlet Line Size and
Length
TABLE I::
RECIP.-ORGANIC
(TECO)
FL-85
300/1800 RPM
vaporizer
Pressure Signal
+3 In.
-10/+16 In.
10 In.
Expander pad
Adapt to Spline
CCW
1 to 1
1 In. ID x 5 Ft.
(1) vertical distance from condenser
outlet port centerline to pump drive
centerline - positive value when pump
drive is above condenser port
TURBINE-ORGANIC
(ALRC )
RECIP.-WATER
( S ES )
AEF-78
16,800/31,200 RPM
Water
400/2500 RPM
Accel. Pedal-
Metering orifice
vaporizer
Pressure Signal
Unknown
+5 In.
 Unknown  -3 1/2/+13 1/2 In.
 10 In.    LOW 
 Gearbox pad  Bracket 
 Spline   V-Belt 
  CW    CCW 
 1.85 to 1   1 to 1 
1 1/4 In. OD x (Unk.) 3/4 In. ID x (Unk.)
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-------
CAPACITY
Flow Rate - Min. Speed
(N) (2)
Flow Rate - Intermediate
to Maximum Speed (N)
Minimum Flow Rate -
All Speeds
Output Pressure
OPERATING INLET CONDITIONS
Temperature
Pressure
START-UP INLET-CONDITIONS
Temperature
(3 )
Pressure
TABLE II (continued)
RECIP. -ORGANIC
(TECO )
TURBINE-ORGANIC
( AL RC )
7.4 GPM at N =
300 RPM
13.75 GPM at N =
600 RPM

17 GPM at N =
800 RPM
15.4 GPM at N =
1800 RPM
20GPM at N =
16,800 RPM
28 GPM at N ">
16,800 RPM
0.4 GPM at N =
300 RPM
6 GPM at N =
1800 RPM

850 PSIA
1.8 GPM at N =
16,800 RPM
2. 0 G PM at N =
31,200 RPM

600 to 1050 PSIA
100 to 250 of
5 to 90 PSIA
130 to 240°F
12.2 to 32.5 PSIA
-40 to 275°F
0.5 PSIA
-40 to 275°F
1. 0 PSIA
(2) Flow rate varies proportionally with
speed from minimum speed to intermediate speed
(3) Function of system temperature
RECIP.-WATER
(SES )
0.8 GPM at N =
400 RPM
2.5 GPM at N '>
1000 RPM
1 PPM at N =
400 RPM
3 PPM at N =
2500 RPM

1200 PSIA
180 to 270°F
7 to 50 PSIA
32 to 275°F
0.09 PSIA
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Tl
. , I
CAl'DIDATE MAr ~ ~ UALS FO ~ VAPO ~ G ~NERATOR FEED ?U ~? (VANE ?UMP)
            WORKING FLUIDS         
Component              Perchloro-    
   Fluorinol 85  AEF-78   FC -7 5 ethylene  Water
Seals   E. P. R.   Neoprene  E. P. R.  Fluorocarbon Nitrile 
   Silicone   Butyl   Nitrile  (Viton)  Butyl  
        Teflon   Silicone  Fluoro-  E. P. R. 
            Butyl   silicone  Silicone 
            Neoprene          
Vanes   carbon-   carbon-  carbon-  carbon-  carbon- 
   Graphite   Graphite  Graphite  Graphite  Graphite 
   Tool  steel  Tool Steel Tool  Steel Tool steel Stellite 
Bearings       Leaded Bronze Leaded Bronze Leaded Bronze carbon- 
   carbon-   carbon-  Carbon-  carbon-  Graphite 
   Graphite   Graphite  Graphite  Graphite     
Housing  440C  stain-  440C Stain- 440C  stain- 440C stain- 440C stain-
(Block)  less  Steel  less Steel less  Steel less steel less Steel
   52100 steel  52100 steel 52100 Steel 52100 Steel    
Side plates Carbon-   carbon-  Carbon-  carbon-  carbon- 
   Graphite   Graphite  Graphite  Graphite  Graphite 
        Leaded Bronze Leaded Bronze Leaded Bronze    
Impeller  cast  356 Alu- Cast 356 Alu- Cast  356 Alu- cast 356 A!u- cast 356 Alu-
   minum    minum   minum   minum    minum  
   (Anodized)  (Anodized) (Anodized) (Anodized) (Anodized)
Rotor   52100 Steel  52100 Steel 52100 Steel 52100 steel 420 stain-
   420 stain-  420 Stain- 420 Stain- 420 Stain- less steel
   less  steel  less Steel less  steel less Steel    
   Tool  Steel  Tool Steel Tool  Steel Tool steel    
Drive Shaft Nitrided   Nitrided  Nitrided  Nitrided  Greek  
   Nitralloy  Nitralloy  Nitralloy Nitralloy Ascoloy 
   carburized  carburized carburized carburized    
   SAE 8620   SAE 8620  SAE 8620  SAE 8620     
HousingJ Main Cast  356 Alu- cast 356 Alu- cast  356 Alu- cast 356 Alu- Cast 356 Alu-
   minum    minum   minum   minum    minum 
   C'Jst  Tron   Cast Tron  Cast  Iron C2lst Iron  (Anodized)
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-------
TABLE IV
CANDIDATE MATERIALS FOR VAPOR GENERATOR FEED PUMP (GEAR PUMP)
        WORKING FLUIDS       
Component           Perchloro-   
  Fluorinol 85 AEF-78   FC-75 ethylene Water
Seals  E. P. R.   Neoprene E. P. R. Fluorocarbon Nitrile
  Silicone   Butyl  Nitrile (Vi ton)  Butyl 
       Teflon Silicone Fluoro-  E. P. R.
         Butyl  silicone Silicone
         Neoprene       
Gears  Nitrided   Nitrided Nitrided Nitrided   
  Nitralloy   Nitralloy Nitralloy Nitralloy   
  Carburized  carburized carburized carburized   
  SAE 8620   SAE 8620 SAE 8620 SAE 8620   
       Leaded Bronze Leaded Bronze Leaded Bronze   
Bearings carbon Graph. carbon Graph. carbon Graph. carbon Graph.   
Housings cast  356 Alu- Cast 356 Alu- Cast 356 Alu- cast 356 Alu- Cast 356 Alu-
  minum    minum  minum  minum  minum 
  (Anodized)  (Anodized) (Anodized) (Anodi zed) (Anodized)
Impeller cast  356 Alu- Cast 356 Alu- Cast 356 Alu- Cast 356 Alu- cast 356 Alu-
  minum    minum  minum  minum  minum 
  (Anodized)  (Anodized) (Anodized) (Anodized) (Anodized)
Drive Shaft Nitrided   Nitrided Nitrided Nitrided   
  Nitralloy   Nitralloy Nitralloy Nitralloy   
  Carburized  carburized carburized carburized   
  SAE 8620   SAE 8620 SAE 8620 SAE 8620   
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   0     500    1000    ISO 0    2000   
         EXPAND£,~  SPEED ---- RPM     
ENG. REPORT NO.    q   r        CURVE TITLE        
 APTD-1357              FLOW R£QUIRE'M£N -r S
DATE                  ORGAN Ie FLUID   
 12-5-72               R£CIPROCATOR. - TECO
                        ---.--.-  
PREPARED BY RMR              FIGURE NO.  i      

-------
C.ltlndustries @ Chind;" Evans Ine C C.ntrol Systems Division
~
o
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VA R I A 13 L.. ~
\1.4 N£
ORGANIC
TURf3INE.
DISPLAC£ M£NT
PUMP
FLUID
(ALRC)
DATE
12-5-72
PUMP
AT
£FF'ICI£"NCY
3/) 200 RPM
PREPARED BY RMR
FIGURE MO.

-------
Calt Industries Inc @ Chandler Ev,ns Inc Contral Systams Division .
I
~
--L
I I
+-1--
-- ----- -- -4-.--
, I
L r j~ I --+- !_L-r!_--
100 l. '--tt! -U~.~JTd R ---- - LL-J. -- !
'r-----1._- . --LlL_-II' -- -- --_U-W- MIL - - 56 2 .~-!
U I I i I I I ' J JI4 I I
~tr f~~I=LilJ '-ij--r- --~--I
80 1-~rtLU~-- ~-?~-~---+.:-
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* ~-il- I .. . / ~/ v- - Lr. J---
~ 60 1-+-1-+ . / L Li
g ~Jj- . //. / / ct=fl=i---
I L I ~- -L-------1
~ .1. ---,--, '-7 / " .I I____i_-e--


~ R~ICi'~--~7~r: . -- I J_-~ 1~-
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[--IT 1--,- r~-- -()---l -=== - ]
o L-~]-_J_-___!~=l_- --- (~- j--t- -----L-- _r:-~L-\ -

o 5 10 15 20 25
MACHINE LOAD - LBS
ENG. REPORT NO.
APTD-1357
CURVE TITLE
REPORT TITLE
DATE
12-5-72
PUMPING GEAR SCUFFING
VS
MACHINE LOAD - LBS
PREPARED BY RMR
FIGURE NO.
34
4

-------
.,
" "..... ',~":,,,: "'.,.' -..J.
Colt ladostrlll'oo ~ Q....~r Em. ,.. Co.tro' Spttm. D~IoI..
  INLET TEMPERATURE:85-105°F     
 - - INLET PRESSURE: 20 PSIG     
  GEAR STAGE PRESSURE RISE: 800 PSI   
 80          INITIAL CALIBRATION 
           MIL-5624-JP4 AND 
           FLUORI NOL 85  
c\C         .---     
1       V       
>- 60     ./       -  
u    V          
z    /          
w              
......              
u              
......    /           
LL               
LL      FLUORINOL 85 AFTER ONE HOUR 
w            I I  
 40   -- -        
....J   /'        I I  
....J          FINAL CALIBRATION 
«          
~           MIL-5623-JP4  
w            . .  
>       l
-------
!- -
Colt Industries € Chandler Evans Inc Control Systems Division
~ 
\U 
,~ 
I 
~ 
(f) 
~ 
a 
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NET POSITIVE SUCTION HEAD
zs
INLET --- FeET:
AT PUMP
REPORT TITLE
MODEL MFP-/SO

IMPELLE:.R.

PER. FOR? MANCE
CURVE TITLE
IMPELLER HEAD ,'?/s£.
- vs-
NPSfL

36
ENG. REPORT NO.
APTD-1357
DATE
12-5-72
PREPARED BY RMR
FIGURE NO.

-------
~.-"-" "--
PU'--,-_4_--- ,,~ .- .....- ,~. . p
Call Industries Inc @ Chandler [vans Inc Contral Systems Division
100
I-I
I I
I
t=
;: 60 I
LL I
W ---- -f--t--f--
I
l I
~ I --LLLLI '--LtF F - 7"
90 ljd-+ J-::::;;::I _I
U_-~ vc Lu~dB1L, O::::::U"L~i5L --,-+
LJI - -11 -i~l---I-~, ~I 1;1IY !--I -h. I II I
- -++--1-1 A'/ II' 1 r----_L. . !..L!---
80 I_-.J_L- L-t ! i I I I J-!---
I iJl/ 1 I L 0 0 pel R I C EL
U If I l_'
1-4 i I I I I [
70 ill I I +Tl
I liLh' Lf- I Ii
't-II I II f ~----I-I---t=1
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5 0 I ~E R LL ./"Iq ~E F n~ U FUR 10 H d s k N [ U R 1\
l_.--LLI . /V.;""--I I I I
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40 ~~-tl- ~/I L r+ I "I T ST) -~---
r I I I

30 __L_u~T-il fLm - --tJ.

o 1000 2000 3000
PUMP SPEED - RPM
NCE)
0\0
>-
U
Z
W
......
U
ENG. REPORT NO.
REPORT TiTlE
CURVE TITlE
AP T D- 1 35 7
DATE
12-5-72

PREPARED BY
~~FP-150-2
PUMP EFFICIENCY
FIGURE "0.
37
u
-.
--
---.-
.._~-
------
----------------- -------- -
--

-------
e.lllad..lrI.. 1ft. @ ~""Ior £1'" ,.. elllr.. Spbm. D~bl..
    lEGEND      
  8--8 NO WEAR      
  - - X--X WEAR OR EVIDENCE     
    OF OVERHEATING ON     
    SURFACE      
 700          
       X    
 600          
 500          
;;; 400        - 
       - 
Cl..           
I           
a 300      0    
«          
0           
..J           
 200          
 100          
 0          
  0    1000  2000   
  SURFACE SPEED-FEET PER MINUTE    
ENG. REPORT NO. REPORT TITLE  CURVE TITLE   
        ROTATI ONAl WEAR
 APTD-1357     TEST:NITRIDED NITRAllOY
DATE        VS . RE SIN IMPREGNATED
 12-5-72     CARBON GRAPHITE IN
     FlllnRHJnl s
-------
:.\.':\'.:",',. '~".,.~. '.'
. '~,'i. ;'v''':'''~' '{"; .:<,,:~'~I~
Colt "'.,1rI1I In. @ C/laDjI,: bu. Ia. C,aIr,l Sp!olll DIvI,I"
     lEGEND     ' .
           I 
     8--8 NO WEAR      
     X--XWEAR OR EVIDENCE   
      OF OVERHEATING ON  \ 
      5 URFACE     I 
           I 
           I 
           ! 
           I 
           , 
 700           
 600           
 500       X    
......            I
U)            
Cl. 400   C:)    "    
I          
            ;
o            
~ 300           
-!            
    0    <:)    
 200           
 100           
 0           
 0 1000   2000      
  SURFACE SPEED-FEET PER ~~INUTE      
ENG. REPORT NO. REPORT TITLE  CURVE TITLE ROT AT! ONAl WEAR  
     TEST:-440C STAINLESS VS  
 APTD-1357     RESIN IMPREGNATED  
DATE     CARBON GRAPHITE IN   
 12-5-72    FlUORINOl 85     
PREPARED BY    FIGURE NO. 39     

-------
Calt IIju.bIIs '"'@ Clllajl" Enl. I.. CIII1I'1II Sptotu DltlallI
  LEGEND      
  8--8 NO WEAR      
 1000       0 
 900        
 800        
 700        
......    <:)    G 
U1       
a...         
I 600        
0         
«         
3 500        
 400   "     
   v     
 300   0     
       G) 
 200        
    0    0 
 100        
 0        
 0 1000  2000  
 SURFACE SPEED-FEET PER MINUTE     
ENG. REPORT NO. REPORT TITLE  CURVE TITLE ROTATI ONAl \-JEAR
     TEST: NITRIDED NITRAllOY
 APTD-1357 '   VS lEADED BRONZE
DATE      . I N AE F 78
 12-5-72        
PREPARED BY    FIGURE NO.4 0  

-------
~
,'. '\
C.lt Industties I.. @ Ch..dl" E.... I.. C.ntt.1 System. DI.I.I..
     LEGEN D     
     8--8 NO WEAR    
     X--X WEAR OR EVIDENCE  
      OF OVERHEATING ON  
      SURFACE    
 800           
 700           
 600      -     
......            
tf) 500           
CL           
I            
0            
<:(            
a 400   -      -....../  
..J   \.:J     '''''''' .  
 300           
    0      0  
 200           
 100           
 0         -- 
 0  1000    2000    
  SURFACE SPEED-FEET PER MINUTE       
ENG. REPORT NO. REPORT TITLE   CURVE TITLE ROTATI ONAL WEAR 
 APTD-1357     TEST: RESIN IMPREGNATED 
        CARBON GRAPHITE 
DATE      VS 440C STAINLESS STEEL i
   I    I
 12-5-72     I N AE F 78   
PREPARED BY        41   I
      FIGURE NO.  

-------
Colt l.d"lIl" I.. ~
Chandler (vlns Ine: Control Systems Division
     -       
  LEGEND        
  8--8 NO WEAR       
 600      -     
 500           
 400         .,..  
         '-'  
......            
If)            
0... 300           
t           
0          <:>  
«           
0            
...J 200           
     ,      
 100           
 0           J
 o    1000  2000    
  SURFACE SPEED-FEET PER MINUTE      
ENG. REPORT NO.  REPORT TITLE  CURVE TITLE ROT A Tl ONAl WE AR--
       TEST: RESIN IMPREGNATED
 APTD-1357       CARBON GRAPHITE VS
DATE       440C STAINLESS S TE E l IN
 12-5-72      DI 5 TI llED WATER  
PREPARED BY         ---
       FIGURE NO. 42   
            ,

-------
,", .
. ,
C.ltlndll.tri..ln. @ Chandl" E.... In. C.ntrol Systonrs 1111.1...
  LEGEND    
  8--8 NO WEAR    
 600.      
 500      
- .400      
If)       
11..       
I 300      
.£::)    0   0
«     
0       
-,J 200      
    G   0
 100      
 0      
 0 1000  2000 
  SURFACE SPEEO"'FEET PER MINUTE   
ENG. REPORT NO. REPORT TITLE  CURVE TITLE RATl ONAl WEAR
 APTO-1357    TEST: NITRIOEO NITRALLOY
      YS LEADED BRONZE
DATE     IN .PERCHLOROETHYLENE
 12-5-72      
PREPARED BY    FIGURE NO. 43

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VARIABLE SPEED DRIVE
7.20
DRIVE
SHAFT
"'-
~.
16.50
GEAR PUMP
1
tl' II - - -=1'.::- -=- - - '
'I' ,- --.- ,--~
! IF;;;r~-.:.:n.:.::-',=--=-=-~-='!f----=-~
;""'d -=-f--"~-- ,.. .
1,,==---_.,-,' '=='1" I .,-==-
I------';;'~-""" ,'il':""_h.\
'I ,,--_.t-=-..,..----
f':' ~:_--~--'hl- ---
I' ':: :.-
I
~.-;c = -= ~£:::r -=- - -
HYDRAULIC RATIO CONTROL INPUT
~i~ ure
-4
GEAR PUMP ON
VA~IABLE SPEED
DRIVE
TE(O
INLET
<
,
OUTLET
-)

-------
DRIVE
SHAFT
Figure
14.75
7.20 ---1
VARIABLE SPEED DRIVE. I
TWO STAGE PUMP
OUTLET
>
TWO STAGE GEAR
PUMP ON VARIABLE
SPEED DRIVE
TECD
45

-------
,t{~.40R. 3.99R.
BY,PASS---------
VALVE
VAlUABLE
SI'EEO Ofl/V£
6.00
//.50
VANE PUMP ON VARIABLE SPEED DRIVE
SES
~i~ ure ,)

-------
BY-PASS VALVE
_(m
WATER
INLET
.-
4.08
-_J
630
-. ~.
-- 3.94 R
TWO STAGE VANE PUMP
SES
CONTROL VALVE
Figure 47

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6R
/ ~:~:T ""
3.33 '\1.. .
A.
T
WATEH >
INLET
- 2.07 R
1
...
a::t.J
t.J..J
rf-
,c:.::>
3:0
A
--_.-----
VANE STAGE
VANE PUMP WITH
INDUCEP BYPASS.
SES
Figure 48
6.48
JET INDUCER
SECTION A-A

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15.10 -
T

4.28

J
TWO STAGE VANE PUMP
TWO STAGE VANE
PUMP ON VARIABLE
SPEED DRIVE
ALRC
Figure 49
7.60
VARIABLE SPEED DRIVE
-~ -----..------.------
DRIVE SHAFT

-------
SECTION B-B
7.63MAX.~
SECTION A-A
VARIABLE DISPLACEMENT
VANE PUMP
ALRC
~i~ ure 50

-------
ENG. REPOJ{T NO.
APTD-1357
DATE December 5, 1972
APPENDIX A
September 15, 1972
operation of a
Differential/variable Speed Drive Combination
130015
REV. '165
-A-

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130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
ANALYSIS OF VARIABLE SPEED DRIVE WITH DIFFERENTIAL GEAR
TRAIN
The speed range of a variable speed drive can be extended
by employing subtracting differential gears (opposite
rotation) in the drive train.
To achieve the speed range multiplication desired for
the Rankine cycle feed pump systems being studied under
EPA Contract No. 68-01-0430, the arrangement shown in
Figure A-I was selected.
The variator output speed is
multiplied by 4 and the rotation reversed before enter-
ing the differential.
Drive pad power is fed directly
into both the variator and the other differential input.
The effect of employing these parameters is illustrated
in the curve of Figure A-2 which has the TECO system
(reciprocating expander, organic fluid) requirements
imposed upon it.
A drive turndown of 12.4:1 can be
obtained through a variator turndown of 5:1.
A-I

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
However, the speed range advantage is achieved at the
expense' of increased power loss and oversizing of the
variator.
The analysis contained in the ensuing pages develops
this thesis.
To better follow the analysis, refer to
the schematic of Figure A-l.
is shown for simplicity.
A bevel gear differential
130015
REV. 1/65
A-2

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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
SYMBOLS
F = Force
T = Torque
r = Radius
Tj = Efficiency
HP = Horsepower
N = speed
Ii = Speed Ratio
Subscripts refer to elements in system.
TpUMP
TA . = TB = 2
= TSp
2
= T
D
  TpUMP ( nsp + A + c)   
TSp = 2   
,     
  TSp, NSp, N ( nsp + A + C)
  TpUMP SP,
HPSp, =   =   
 63000  2(63000) 
130015
REV. 1/65
A-3

-------
ENG. REPORT NO. -
APTD-1357
DATE December 5, 1972
FDrD = TD
FErE = TE
FE = FD
r
~= R
r . G
D
T - F r = F r R
E - DE. D D G
=
T
D r R
D G
r
D
= T R
D G
Consider "A" leg of circuit removed.
The "B" leg will,
therefore, only transmit power to drive the pump.
T =
E
R
G
T
PUMP
= T .
v2
2 .
TlB + C + D + E
HPv' =
2
T. N
V2 V2
63000
=
T Nv
RG PUMP 2
2(63000) ( 11B
+ C + D + E)
130015
REV. 1/65
A-4

-------
ENG. REPORT NO.
APTD-1357
DATE December. 5, 1972
N
V2
= R
V
N
VI
R = variator Speed Ratio
V
11V = f (RV)
HP 8 =
V,
HP .
V2
11v
HP . =
V.
R T N R
G PUMP V. V
2(63000) 11 (11 C
V B + +
D + E)
N
V.
= N = N
SP. DRIVE PAD
Since the power in the "A" leg is recirculating, it
must also be operated on by the efficiency in the "B"
leg.
o
o 0 Total HP in variable speed drive (VSD)
=HP
V.
+
HP
SP.
TlV (
B + C + D + E)
HPVSD =
T N
PUMP DRIVE PAD
2(63000)
[11 SP + A + C
L Tlv ( TlB +
: :GDR: E~
130015
REV. 1/65
A-5

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""-
...w
<0
-0
-0;
~
VI
MFP-150 ON VARIABLE SPEED TRANSMISSION WITH DIFFERENTIAL
11
11
11
11
~
I
0'\
condition N N R Q .6P  HP T R I\,    HP
(TECO) DP P    P P P G V A B VSD
          (TPI   
1 900 1065 1. 182 1.3 850 24 2.685 159 4 .841 92.2 98 97 5.51
          (1/1.19)    
2 900 3225 3.59 7.3 850 71. 5 5.06 98.8 4 2.045 89.6 98 97 7.44
3 1800 5852 3.25 14.6 850 79 9.15 98.4 4 1. 875 89.9 98 97 13.7
4 2400 6716 2.8 17 850 78.5 10.72 100.7 4 1. 65 90.3 98 97 16.6
5 6000 6716 1.12 17 850 78.5 10.72 100.7 4 .81 86 98 97 24.3
          (1/1. 233)    
6 6000 1750 .292 3.2 850 52.5 3.02 108.7 4 .396 85.3 98 97 16.03
          (1/2.52)    
RECIPROCATING EXPANDER - ORGANIC FLUID (TECO)
rr,
z
C')
:;0
['1'1
"0
o
~
~
z
o
I
~
'tI
8
tJ
I
t-'
VJ
U1
....,J
o
»
~
tr1
tJ

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
DRIVE TRAIN EFFICIENCY
HP
OUT
11 DRIVE =
HPIN
=
HP
P
HPVSD - HPRECIRCULATING
=
HP
P
HPVSD - HPSP,
T N 11
HP = P DP SP + C + A
SP, 2(63000)
=
Tp NDP
128,571
 T N HP HP HPVSD HP -HP I1DR
Condition SP, VSD SP,
P DP  P   'Yo
1 159 900 1. 09 2.685 5.51 4.42 60.8
2 98.8 900 .692 5.06 7.44 6.75 75.1
3 98.4 1800 1. 377 9.15 13.7 12.32 74.3
4 100.7 2400 1. 88 10.72 16.6 14.72 72.9
5 100.7 6000 4.7 10.72 24.3 19.6 54.7
6 108.7 6000 5.07 3.02 16.03 10.96 27.55
. 130015
REV. 1/65
A-7

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
SYSTEM EFFICIENCY
Condition 1IDR 11 PUMP  11
SYSTEM
 % % %
1 60.8 24 14.6
2 75.1 71. 5 53.6
3 74.3 79 58.6
4 72.9 78.5 57.1
5 54.7 78.5 42.9
6 27.55 52.5 14.44
SYSTEM EFFICIENCY COMPARISON
WITH AND WITHOUT THE DIFFERENTIAL
1
2
11 11
System System
with without
Differential Differential
14.6 22.1
53.6 64.0
58.6 71. 0
57.1 71. 0
42.9 67.5
14.4 44.8
Condition
3
4
5
6
130015
REV. 1/65
A-8

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1-
DRIVE
PAD~
Ndp
CHAIN
SPl
HP
vi
SPEED
VARIATOR
N
P
\
GEAR DIFFERENTIAL
HP
out
PUMP
VARIABLE SPEED DRIVE WITH DIFFERENTIAL GEAR TRAIN
 6
 5
o 
H 
E-t 
~ 4
Q 
rz:I 
rz:I 3
~
U) 
Z 
0 2
H
U) 
U) 
H 
::E: 1
U)
z 
~ 
8 0
-0.5
-1
FIGURE A-l
      I ,  
   I     
   I     
   0'1     
   ~     
    0+~   
    I    
     ~.I'   
     .I'   
      ,,+:   
      :I   
      ,-r   
      I I   
      i1.:  
  ,J       
      1."/.. iii~ 
-I        -
 I        
!         
o
0.5
1.5
2.5
3.0
2.0
1.0
VARIATOR SPEED RATIO
FIGURE A-2
A~9
VARIATOR SPEED
MULTIPLICATION
THROUGH GEARS

-------
130015
REV. 1/65
ENG. REPORT rw.
APTD-1357
DATE December 5, 1972
APPENDIX B
TECO Seal Compatibility Tests
-B-

-------
THERMO ELECTRON
CORPORATION
85 FIRST AVENUE
WALTHAM. MASS. 021!54
TEL: 617 890-8700
CABLE: TEECORP
September 13, 1972
L.A. DUford
Colt Industries, Chandler Evans
Control Systems Division
Charter Oak Boulevard
West Hartford, Connecticut 06101
Dear Bud:
The compatability tests of your samples with Fluorinol-85
have been completed and the results are shown in the enclosed memo-
randum from our chemist to Dean Morgan.
Test conditions are listed and the results as well as
clusions and recommendations are given. A Iso included is a
materials recommended for use by TECD.
con-
list of
Yours truly,
Luco R. DiNanno
Development Engineer
mg
Enclosures
cc: K. Barber
B-1

-------
MEMORANDUM
DA TE:
September 5, 1972
TO:
Dean Morgan
FROM:
Alexandra Zakak
SUBJECT: Compatibility Test or-Some Rubber Products
Summary
.J.

Samples of preformed packings ..,- of both fluorosiliconeand silicone com-
pounds were tested in F-85 and a lubricating oil (v. ratio 10/1) in the
presence of air at 250°F. After a testing period of 17 days (continuous
heating) both fluorosilicones (LS53 and LS63) were much softer and v,,-ere
lightly attacked at the bottom in F-85 immersed portion. Th~ silicon
compound no. '5455-7 showed to be more resistant in.F-85. A light
softening occurred in the portion of the ring immersed in liquid F-85.
Conclusions and. recommendations are also given.
Re sults
Test conditions and results of visual observation of tested samples are
summarized in Table 1. Each sample was sealed in air in a pyrex te st
capsule. Both fluorosilicones samples LS53 and LS63 were attacked in the
bottom immersed part and were much softer. The silicone compound no~
:-$455-7 was very lightly softer, but gained some weight due to swelling,
about 11%. with a light change in dimensions. The liquid F-85 turned to
a very light or light brown color. . .
"
Conclusions
1.
. F1uorosilicone rubber, Dow Corning LS53 was attacked at the bottom
portion of the sample, immersed in F-85. The material becaTne I!1.uch
softer.
2.
Fluorosilicone rubber, Dow Corning LS63 was very lightly attacked at
the bottom portion of the sample, immerse~ in F-85. Thematerial
became much softer. .
3.
Silicone rubbcr, Parker no. :'5455-7 seemed not to bc attackcd by F - 85
liquid or vapor, percent swelling was approximately equal to 11 %. No
major change in dimensions occurred.
. .
::'Sce Appendix for inforn1ation ,dn m;:;.nu[ac'.:urc;rs.
B-2

-------
TABLE I
TEST CONDITIONS
Test Conditions:
Solution: F-85 and lubricating oil
Temperature: 250°F
Duration: 17 days
(v. ratio 10/1)
Specimen     Atmosphere  
No.   Material  in seal Visual Obsc nration
 ...       
. ....      the rubber was much
779  Dow Corning  air
  LS53, fluorosilicone rubber  softer, lightly a.ttacked
  (- 2" x 0.07" O. D. )   at bottom in liquid
       immersed portion,
       brownlsh 'material ,vas
       sticking on gla s sand
       liquid F-85 turned to
       very light brown
 ...       
780 ""       
 Dow Corning  air the rubber wa s much
  LS63, fluorosilicone rubber  softe r, lightly attacked
  (1. 5" x 0.1" O. D.)   in liquid immersed
       portion. F-85 turned
       , very light brown.
, ......       
781"'''''' Parker No. 5455-7  air the rubber was lightly
  silicon rubber   softer, no apparent
.'  (2 11 x O. 1" O. D. )   change, T-85 turned
       lightbro\vn.
o'
*After test, dimensions changed
*>:'Wcight change ,after test + O.q425 gm
% swelling. - 11%
. .
"
B-3

-------
Recommendations
1.
As a result of the static capsule test, it is recommended to use silicone
rubber Parker no. 5455-7 in the presence of F-85 at 250°F.
2.
Compatibility tests must be run previous to any use of material if
higher temperatures are expected.
,.
. .
)
. ,
..
B-4

-------
THERMO ELECTRON
COMPATIBILITY TESTS OF SOME ELASTOMERIC
AND NON-METALLIC MATERIALS
Recommendations
1. Teflon (TFE) is also recommended to use at temperatures
350°F in the presence of F-85 solution and air.
not exceeding
2.
Teflon fiber (DuPont De NeMours Co., Textile Fibers Department),
hard or soft packing may be used up to 250°F in the presence of F-85
solution in air (respective % swelling -:- 350/0 and 130/0). It is believed
.that Teflon fibers can stand temperatures up to 350°F in the presence
of F-85 and air. More tests are needed.
3.
Al-Si-Mag 840 ceramic (American Lava Co. ) may be used up to 350°F
in the presence of F-85 and oil.
4.
Glass and mineral filled phenolic No. FM4005 (Fiberite Corp. ) may be
used in the system up to 200°F in the presence of F-85 and oil.
5.
Silicone rubber (0 -ring) Parker No. 5455-7 is recommended to be used
in the system at temperatures not exceeding 250°F in the presence"of
F-85 solution and air.
."
B-5

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE December 5 J 1972
APPENDIX C
Gear pump Design
-c-

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
Pump Size
The displacement and proportions of the pump must be
selected to offer the best efficiency over the largest
range of speed and flow operation with pressure rise
constant.
Displacement
The peak overall efficiency of a positive displacement
pump varies with size.
The cause of this variation is
the effect of manufacturing tolerances and operating
clearances, which vary little with size, and windage
and porting losses associated with high capacity
machines.
Gear pumps for low viscosity applications
follow a trend as shown below.
o
~ 80
)-
"
2 E.O
w
-
"
-
1&,.
I&, 40
t..J
..,,,.. NO OF' PUt( EF'f1(.'CNCV
ATTA'N48\.E F'O~ 6e"~ PuMP$
FOR LOW VISCOSITY LlQ,",'OS
~
~
C ZO
t:
...
>
o
o
1.0
2.0
~.O
~.O
5.0
\30015
REV. 1/65
D,SPLACEMCNT - Cue.c 'NCHES Pt~ ReVOLuTI01ll(CIPR)
FIGURE C.,
C-l

-------
130015
REV. 1/65
APTD-1357
DATE December 5, 1972
ENG. REPORT NO.
This peak efficiency occurs at a certain pressure rise
at each speed, the ratio of which remains fairly con-
stant.
The following figure illustrates a typical
variation of a gear pump efficiency with the speed
normalized pressure parameter.
>
"" '0
Z
w
'"
Ii:
....
LaI 40
100
80
20
TYPltAL EFFICIE"NCY
CHA~ACTfjAISTI' FG~
'EAR PUMP FbR LOW
VISCO.,W HI~ p",n~"~
o
1.0 2.0
% DESIGN PRESSuRE" + "OE'SI6H SPt:E:O
F'16UR&: C.,
C-2

-------
ENG. REPORT NO.
APTD-1357
DATE December 5~ 1972
The absolute value of the pressure rise to speed ratio
for peak efficiency has been found to vary with dis-
placement as shown in the following figure.
11
~ .£1
L
~
Ct ."3
:
o
:: .t
L
lit
...
~ ..
:»
.,.
on
w
a: .
n. 0
2 3 4 5
D'SPLACE.M E"T . C"'elC~ I..(HII P&f\ Ravo LuT ION (CI PR)
f"1t8Urtt c.,
From these considerations, it is apparent that for
acceptable overall efficiency, the pump displacement
should be between .2 and 2.0 CIPR.
The selection is
dependent on an iterative analysis which includes:
130015
REV. 1/65
C-3

-------
ENG. REPORT NO.
APTD-1357
DATE
December ,5, 1972
1) The effect of volumetric efficiency on sizing
for maximum flow and for minimum speed.
2) The variation of pump efficiency with speed
(reference Figure C-2).
3) The effect of maximum speed on minimum NPSP.
4) The effect of maximum speed on wear.
As a result of this analysis, the following capacity
ranges were selected for the steam and organic systems.
The limits imposed on these ranges are noted.
The
actual size selection within this range is made in the
following proportioning analysis.
System
CIPR
Limits for sizing
Steam System
(2.5 gpm nominal)
.2 Min.
Smaller units produce
low overall efficiency

Larger units have poor
low speed volumetric
efficiency
.6 Max.
organic Systems
(25 gpm nominal)
.5 Min.
Smaller (high speed)
units require high NPSP

Larger units have low
overall efficiency
1. 0 Max.
130015
REV. 1/65
C-4

-------
ENG. REPORT NO.
APTD-1357
DATE
December 5. 1972
proportioning
The desired efficiencies discussed in the Displacement
Section can only be achieved. if the pump proportions
are correct.
Those proportions critical to a gear pump
design are as follows:
L/DG = The gear length to diameter ratio which must
remain between 1 and .25 for acceptable volu-
metric efficiency.
L/DJ = The gear journal length to diameter ratio which
is only effective up to a limit of 2.
DP = The diametral pitch which produces poor gear
a'ction at values below 8 and inefficient pack-
aging at values over 12.
T = The number of gear teeth which must remain
between 8 and 20 for the same reasons cited for
DP.
130015
REV. 1165
C-5

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
D /D = Ratio of gear journal to root diameter which
J R
must be less than .75 for effective sealing.
These proportions must be matched against the required
pressure rise and flow rate requirements while still
satisfying the following limiting parameters for the
materials described in the Materials Section.
UBL = The unit load on the journal
< 600 psi
PV = The combined load on the journal < 1.5.106 (psi) (fpm)
pvt = The scoring factor for the gear < 300,000
(t = length of path of contact of gears)
U = Gear tip speed which dictates the boost pump
charging pressure required
130015
REV. 1/65
C-6

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
December 5, 1972
DATE
An l8-tooth, 10 DP, gear was selected for both the
organic cycles.
This gear offered the lowest stress
levels throughout the gear and journal while requiring
a net positive suction pressure which can adequately
be achieved by a boost pump.
Both systems use the
same (.9 CIPR) displacement for the single-element
design while the dual element concept reduces the length
of this same gear to effect a .6 CIPR.
Pump Performance
Based on data from gear pumps of the same displacement,
the following performance is predicted for the organic
turbine cycle gear pump.
C-7

-------
APTD-1357
DATE December 5, 1972
ENG. REPORT NO.
Efficiency
The overall and volumetric efficiencies of these pumps
are predicted in the following figure.
'0
>-
U
Z
W ~O
u
-
'"
"-
~
20
130015
REV. 1/65
100
80
o
.1 .2 . '3
PRI:SSURE RISE: -+ SPEED
.5
.4
P5101 RPM
F'16UREC- 4
C-8

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
APPENDIX D
vane Pump
-D-

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
Pump Sizing
The pump displacement and proportions must be selected
to offer acceptable system efficiencies.
The analytical
approach is similar to that used for the gear pump
(Appendix C), however, since there is not as much ex-
perience with vane pumps in high pressure applications
with low viscosity fluids, predicted performance is
based more on a detail loss analysis.
Displacement
Test results for vane pumps in low viscosity service
agree with the more extensive experience previously
presented in Appendix C for Gear Pumps.
This agreement
occurs both in the peak efficiency to be achieved vs.
displacement (Figure C-l) and on the location of this
peak efficiency in relation to the pressure rise vs.
speed ratio (Figure C-3).
It follows, then, that the
displacement range for further proportioning analysis
should be the same as that chosen for the Gear pumps.
130015
REV. 1/65
D-l

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
proportioning
The following proportioning ratios have been established
for the vane pump for the reasons cited.
S/H = vane stroke to height ratio selected at a nominal
value of .32.
Higher values present problems of
vane guidance in the slot, and lower values ad-
versely effect the rotor strength.
S/w = vane stroke to width ratio selected at a nominal
value of 1.6 since both higher and lower values
produce rotor strength problems.
AR = Ratio of vane track acceleration to the centri-
petal acceleration selected at .6 since the vane
cannot follow the cam at higher values, and the
cam loads are undesirably high at lower values.
These ratios are input to a computer program along with
the required performance at flow rate and pressure rise
at a selected operating speed.
Material properties and
mechanical sizing are either input or monitored at the
output to assure sound mechanical design.
These
130015
REV. 1/65
D-2

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
parameters include vane bending and Hertz stress. . The
parasitic losses within the vane stage are calculated
and later summed with the predicted bearing and seal
losses to allow prediction of total power consumption
and resulting overall efficiency.
The result of an iterative analysis of several computer
design studies indicates that the most favorable design
for the Steam Engine is that presented on the following
computer readout sheet.
130015
REV. 1/65
D-3

-------
VANE STAGE PROPORTIONING ANA~YSIS CHG A
INPUT DATA.
INPUT VANE SPEED...............
THEORETICA~ DISPLACEMENT..~....
SLIDING VELOCITY OF VANE TIP...
VANE STROKE TO HEIGHT RATIO....
VANE $TROKE TO THICKNESS RATIO.
MINIMUM VANE THICKNESS.........
VANE MATERIAL DENSITY..........
COEF. OF FRICTION VANE TIP.....
WINDAGE COEFFICIENT............
VANE STAGE PRESSURE RISE.......
ACCELERATION RATIO RADIAL/ROT..
PUMP MODEL NUMBER..............SES
OUTPUT DATA
NUMBER OF VANES.............~..
TRACK RING DIAMETER-MAX........
VANE STROKE...............~...~.
VANE THICKNESS-CALC............
VANE HEIGHT......~......~.i;~.;-
VANE THICKNESS-USED............
VANE BEARING LOAD-TIP;~.;~;;;.;
VANE LENGTH....................
VANE LENGTH TO DIAMETER RATIO..
VANE ROOT DIAMETER-MAX.........
TIP DRAG HORSEPOWER LOSS.......
WINDAGE HORSEPOWER LOSS........
TOTAL-HORSEPOWER LOSS;~........
VANE BENDING STRESS............
VANE HERTZ STRESS.....~;.......
,--- - '~- .-
. ..- '-- _..~-- - '~_-_~'T -.
D-4
5000.00
0.3995
35.00
0.3250
1.6000
U.0400
0.0690
0.0500
1.5600
1200.00
0.60
12.0
1.6042
U. 0 723
0.0451
0.2233
0.0451
Q04.53
0.6470
0.44
1.012
U.1S07d
0.0762
0.2269
7656.7
15J62.27
RPM
CU IN/REV
FPS
INCHES
LBS/CU IN
HP
PSI
INCHES
INCHES
INCHES
INCHES
INCHES
PSI
INCHES
INCHES
HP
HP
HP
PSI
PSI

-------
ENG. REPORT NO.
APTD~1357
DATE December 5, 1972
Performance
Although the peak overall efficiency of the vane pump
is similar to that of a gear pump, the predicted per-
formance characteristics are not similar.
Efficiency
The overall and volumetric efficiency for the steam
engine pump is predicted in the following figure.
The
volumetric efficiency at low speeds is higher than that
demonstrated for a gear pump (Figure C-4) which was use-
ful in conserving power for the larger speed range en-
countered in the steam engine system.
80
100
>-
~ 60
w
u

u..
u..
w
4
.4 CIPR BALANCED
VANE PUMP-WATER
20
o
o
.2 .4 .6 .8 1.0 1.2 1.4 1.6 1.8
~PRESSURE RISE A OPERATING SPEED PSID/RPM
2.0
FIGURE D-1
D- 5

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE
APPENDIX E
INDUCERS
-E-
December 5, 1972

-------
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
Requirements
The inducer requirements to assure proper charging of
the positive displacement pump for each of the Rankine
Cycle Systems must be established.
Tabulated below is
the pump input speed and resulting positive displace-
ment pump tip speed.
This parameter defines the pres-
sure rise required from the centrifugal stage which,
combined with the flow, establishes the Specific Speed
Parameter.
Finally, the system inlet pressure above
vapor pressure combines with the aforementioned flow
and speed conditions to establish the Suction Specific
Speed parameter.
These two parameters, Specific Speed
and Suction Specific Speed, define the type and degree
of complexity of the centrifugal pump design.
    Charg-   
  pos Displ Flow ing   Suction
  Tip Speed Rate Head specific NPSH Specific
System RPM fps 9E!!L ft. speed ....!b. speed
Steam 4000 35 2.5 38 412 1.188 5,558
organic 8000 62.8 28 122 1150 8.317 3,653
Turbine
organic       
Recipro- 6660 46.5 17 67 1170 4.27 9,244
cator       
130015
REV. 1/65
E-l

-------
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
From this analysis, it appears that all cycles have
manageable conditions as far as suction conditions are
concerned.
The NPSH was determined by the physical
head in the installation plus the pressure above vapor
. .'
pressure at the minimum subcooling condenser conditions.
Centrifugal inducers were sized for each of the three
applications.
As the following descriptions will show,
they all are a nominal three inches outside diameter
and, therefore, consume the same envelope despite the
wide variation in operating requirements.
. The organic Turbine inducer is a three-bladed, un-
shrouded impeller.
It is a specialized mixed flow
design which has a cone for the hub and blade tip con-
figurations.
The blades, themselves, are perpendicular
to the hub surface.
The unshrouded design minimizes
axial loads due to unequal pressure gradients on the
hub or tip shroud.
Also, close running labyrinth
seals are eliminated.
130015
REV. 1/65
E-2

-------
... /20
b..
UI 100
In
Q:
C
<
IIJ
:r.
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
collector.
This impeller discharges into a constant area toroidal
such a collector has better efficiency at
part flow than a conventional volute or vane type
diffuser.
It has no circumferential pressure gradient
around the impeller and, therefore, no radial loads are
imposed on the bearings.
The performance and detail geometric proportions of this
centrifugal inducer are described in the following set
of figures.
.53 DIA
~ - --.. . ._u
ORGANIC
TUR6INE"
SY5T~M
Ff:E"D
80
I-
~ 2.4
2
- <:'.0
60
40
~
w 1.6
'}
~ 1.2.
I.U
If 8
o
:r. .4
20
o
2000 4000 6000
SPEED RPM
eoco
E-3
L
i r. 370

I
3,008 D,A,
PUMP
INDuCeR
2.8
o
ZOOO 4000 (,000
SPEED RPfV1
8000

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
This centrifugal inducer would also satisfy the require-
ments of the organic reciprocator system with a little
margin.
Actually, the outside diameter could be re-
duced to 2.7 inches and still adequately charge the
positive displacement section of the organic recipro-
cator boiler feed pump.
This application also has the possibility of being
satisfied by the same centrifugal inducer sized for the
steam system.
This inducer consists of a four-bladed,
unshrouded radial impeller which discharges into a
constant area toroidal collector.
A radial impeller was selected because it offers the
best overall efficiency in this specific speed range
while still satisfying the suction requirements.
The
reasoning for the other geometrical considerations is
the same as presented for the organic Turbine System.
The performance and detail geometric proportions of
this inducer are described in the following figures.
130015
REV. 1/65
E-4

-------
[
l:!
i"
:~I
[,
i~
IJ
11
I

{
l;:

w 40
'"
tr
~ Zo
Iu
J:.
130015
REV. '165
o
ENG. REPORT NO.
APTD-1357
STEAM
SYSTErv\
FE£"D
1000
2000
3000 4000
SPeED RPr1
PUMP
...
':) .I~
Q.
'Z
~ ,08
~
f
::: ,04
a:
o
~
E-5
DATE' December 5 J 1972
L ~ l~20 p'A
J:A --1
-J ~ ,/0
INDUC£R
o
3000 4000
1000
2.000
SPE'E'D RPM

-------
,:..
'"" /00
I.L.
II.! 80
III
IX bO
o 40
<
....
:to 20
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
The performance of either of these inducers, when
applied to the organic Reciprocator System, is shown
in the following set of figures.
It should be noted that the reported test results, pre-
sented in another section of this report, agree with
this performance and the table on pageE-l.
ORGANIC
R~c IPRoCATOR S'fSTEM
FE" E"D
PU M P 1 NDuC E:R
/20
5 1.2
Q
~ 1.0

;;; .,8
~
~ .6
I.u
11\ .4
oc
o
:I: . 2.
/RADIAI.
:/ IMPE'LL..e:R
~
f'I;XED
F'LOw
I MPE:LLE
~ RA DIAl..
IMPEl.l..E~
?/
~
~
o
2000 4000 6000
SPEED R PM
o
2000 4000
SPE"IOO R PH
6000
E-6

-------
ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
Still another alternative is available for the steam
system and that is to employ a jet inducer.
This in-
ducer would use bypass flow from the positive dis-
placement pump to induce floW at its own inlet by a
venturi effect. Shown below is the schematic of this
system, together with the sizing of the inducer and its
predicted performance.
 100 ~ 
...  
'"-  
...  
V) SO 
Q::    
£)    
c(    
\.oJ    
J:    3
 o  2
  5 YS n: 1"\ F"LOW c;p,",
This presents obvious potential improvements such as
using a pintle nozzle in the jet inducer to fulfill the
bypass function for the positive displacement pump.
130015
REV. 1/65
E-7

-------
ENG. REPORT NO.
130015
REV. 1/65
APTD-1357
DATE December 5, 1972
APPENDIX F
VARIABLE DISPLACEMENT VANE PUMP
-F-

-------
I
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
Pump Size
The analyses presented in Appendices C and D establish
that .9 cubic inches per revolution is the desirable
displacement for the organic turbine cycle pump.
Chandler Evans has a pump of this capacity, the per-
formance of which is recorded below.
Pump Performance
The following curves show the performance of the MFP-
330 variab+e displacement vane pump in the full stroke
position (Figure F-l) as modified by partial stroke
operation (Figure F-2). The dotted lines show perfor-
formance improvements to be attained with low density
and hydrodynamic vanes.
100
o
.8
.6
.4
100 >-
v
 2
 lIJ
 U
80 G:
 u.
 Cd
 I.IJ
"0 ~
 o
 ~
 t,;
40 
 J
 ..J
 :>
20 l!..
 u.
 o
 ~
o 
>- 60
u
z
w
v 40
I..L.
l!..
LU 2.0
E:'XIST NG PI) P
LOW cNS1T'I YA~e;s
HYO OPYNAM C VAN~S
80
FIGuRe- F-/
FIGU 'f! F-Z
,04 .08 .12. ,I"
PRESSuRE..:,. SPEED PSID/RPt1
,.f', I
,2
FRACTION OF FULL STROKE
130015
REV. 1/65
F-l

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
 System Performance     
 The following table presents the predicted variable dis- 
 placement pump system performance for the organic turbine 
 cycle engine.     
  18 gpm Idle Speed Pump  
     Maximum Existing  
 Pump .pressure System Pump Pump LOW Hydro-
operating speed Rise Flow Flow System Density dynamic
Point RPM PSI GPM GPM Efficiency vanes vanes
1 5256. 1050 1.8 18.4 22 25 36
2 5256 1050 20 18.4 67 74 86
3 7500 1050 28 26.3 71 77 87
4 9756 1050 28 34.3 66 71 83
5 9756 1050 2 34.3 19 19 25
1 ' 5256 600 1.8 19.5 20 33 38
2 ' 5256 600 20 19.5 68 74 86
3' 7500 600 28 28 65 70 82
4' 9756 600 28 36.2 60 65 78
5' 9756 600 2 34.3 18 19 23
130015
REV. 1/65
F-2

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
APPENDIX G
cycle Fluid properties and Comparisons
130015
REV. 1/65
-G-

-------
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>- 
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z 
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130015
REV. 1/65
ENG. REPORT NO.
". ..,,- "'. , ",.~:" '"
APTD-1357
DATE December 5. 1972
APPENDIX H
piston Pumps
-H-

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
The parametric study of piston pumps operating on low
viscosity fluids, from which the curves in this section
were derived, proceeded from a review of actual per-
formancedata acquired at Chandler Evans and its English
licensee, Dowty Ltd..
The development by Thermo Electron of a variable dis-
placement piston pump for the Rankine cycle automotive
application was also included as input to this investi-
gation. The) TECO data was obtained from their published
reports.
Most of the pumps investigated were of radial' piston
configuration operating on aircraft fuels having vis-
cosities around 1-2 centistokes.
Efficiency and net positive suction head as a function
of pump displacement were the parameters of prime con-
cern in this study.
drawn:
The following conclusions were
130015
REV. 1/65
H-l

-------
130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
1.
Efficiency
Manufacturing tolerances and operating clearances,
which contribute to leakage losses, vary little
with pump size.
For this reason, the peak overall
efficiency of a piston pump increases with dis-
placement.
windage and porting losses have a more direct
relationship with pump displacement.
The net effect of all of these losses tends to
cause the peak overall efficiency to become ~symp-
totic to the 90 percent line as size increases.
This is shown in Figure H-l.
Figure H-2 depicts both volumetric and overall
efficiencies as functions of a normalized pressure
parameter for a piston pump of 2.3 cubic inches per
revolution (CIPR) displacement.
H-2

-------
130015
REV. 1165
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
Figure H-3 indicates the value of this normalized
pressure parameter at which peak overall efficiency
occurs, with respect to displacement.
All of this points to a large, slow piston pump as
being more efficient.
2.
Net positive Suction Head
Inlet pressure requirements for piston pumps can be
determined from Figure H-4.
If spring loaded valves
are used, the pressure parameter will follow a
steeper curve than shown.
It can be seen that a
small, slow pump needs ~ess inlet head for satis-
factory performance.
H-3

-------
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               -.-
ENG. REPORT NO. REPORT TITLE    CURVE TITLE    
       I   PISTON PUMP  
APTD-135 7        EFFICIENCY VS 1
DATE       I   DIsPLACEMENT 
12-5-72     I        
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    PRESSURE RI SE + OPERATING SPEED 
              ...-
ENG. REPORT NO. REPORT TITLE    CURVE TITLE 
 APTD-1357         EFFICIENCY
          VS
DATE          6P/N FOR PISTON PUMP
 12-5-72         2.3 CIPR.
PREPARED BY             
         FIGURE NO. H-2

-------
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   DISPLACEMENT - CU. IN. PER REVOLUTION (CIPR)
ENG. REPORT NO. REPORT TITLE      CURVE TITLE   
         6 PIN VS CIPR 
 APTD-1357       FOR P IS TON PUMPS AT PEAK
DATE         OVERALL EFFICIENCY
 12-5-72           
PREPARED BY        FIGURE NO. H - 3 

-------
CoR lodustrlesl.. ~ Chlll'.I" Ems In. Control Sys~..s Divisio.
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  DISPLACEMENT - cu. IN PER REVOLUTION (CIPR)   
ENG. REPORT NO.  REPORT TITLE     CURVE TITLE    
APTD-1357        NPSP/N2 VS   
         CIPR FOR PISTON PUMPS
DATE              
12-5-72             
PREPARED BY        FIGURE NO. H - 4   

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130015
REV. 1/65
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
APPENDIX I
Two-Stage Pumping
-1-

-------
ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
The high overall pump efficiencies specified by Contract
No. 68-01-0430 tax the performance capability of the
ordinary positive displacement pump, especially at low
speeds.
Adding to the problem are the inefficiencies
accruing to a variable delivery pump, either running at
part displacement or operating on a variable speed drive.
Because of engine demands, the work performed by the
feed pump is necessarily high, especially in the ALRC
system.
Efficient pump operation contributes substan-
tially to economic engine performance.
The variable delivery mode of operation in some of the
pumping systems analyzed in this project is accomplished
by a fixed displacement pump on a variable speed drive.
Toward optimizing the efficiencies of this combination,
consider the following:
1.
Limit the turndown range of the variable
speed drive to stay at or near maximum
drive efficiency.
130015
REV. '165
I-l

-------
ENG. REPORT NO.
APTD-1357
. DATE December 5, 1972
2.
Limit the turndown range of the pump to
stay at or near maximum pump efficiency.
Accumulators may be used to handle short~
term transients and bypass valves to handle
situations below steady-stage running con-
ditions.
3.
Since in normal vehicle operation, the feed
pump output is in the low flow fange, devise
a pumping system which calls in full capacity
only at high demand.
The ALRC system require-
ments displayed in Figure I-l show the logic
of this approach.
Item 3, above, can be achieved by a variable displace-
ment pump, however, especially in the case of a vane
pump, the efficiency penalty from operating at part dis-
placement is too severe.
Accomplishing this with fixed
displacement pumps produces, in essence, a two-displace-
ment pump.
This can be done with any type of pump.
130015
REV. '/65
I-2

-------
ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
A review of Appendices C and D suggests a method of
"staging" pumping elements to optimize efficiency.
If the discharge of a pumping element is directed to
the inlet of another equal or slightly smaller element,
the output is that of a single element and each supports
only half of the total pressure rise.
a schematic of such an arrangement.
Figure I-2 depicts
When the demand exceeds some predetermined level, the
flow paths are switched so 'that each element is pumping
I
independently of the other;
In this condition, the full
pressure rise is borne by each element.
A two-element pump can thus be operated either in
series or in parallel.
The advantage of this technique can be seen by referring
to the efficiency versus pressure
-
.
speed curve on
page D-5 of Appendix D.
within a given range of dis-
placements, the peak efficiency occurs at a distinct
value of this ratio.
The peak efficiency can, therefore,
130015
REV. 1/65
I-3

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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
be obtained at several points within an operating
envelope by varying both speed and pressure rise.
This
basic information was used in plotting the curves in
Figure I-3 for specific speeds and pressures.
It can be seen that by varying the pressure rise across
each element, the best efficiency characteristic of the
entire pump can be shifted with speed.
As an additional advantage to this method, the speed
ratio range of the variable speed drive can be narrowed,
which tends to optimize drive effi'ciency as well.
The efficiency curves for two-stage operation presented
in the main body of this report were plotted by follow-
ing this line of analysis.
Installation studies were
made, some of which are illustrated in Figures 45, 47
and 49 in the main body of the report.
\30015
REV. 1/65
I-4

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ENG. REPORT NO.
APTD-1357
DATE December 5. 1972
It thus remains to select the parameters that will con-
trol the switching point and to provide a physical means
to effect smooth transitions between series and parallel
operation.
These problems will be resolved in cooperation with the
system contractor while the pump is being integrated
into the complete system.
However, conjecturing a bit,
the following control modes are suggested:
1.
I
organic Fluid Reciprocator - TECO
1.1
It was noted in the TECO system that the
intersection of the efficiency curves for
series and parallel operation varied with
expander speed.
Since discharge pressure
is constant, engine flow is ultimately
established by throttle position.
The
throttle mechanism can also load a spring

against which a flyweight actuator may
I
operate. Thus, for each flow rate,
switching will occur at a unique and
I
different engine speed.
130015
REV. '/65
1-5
"

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130015
REV. 1165
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
1.2
A simpler method would establish the switching
point strictly by throttle position.
There
would be some sacrifice of efficiency at cer-
tain conditions, but this may be outweighed
by the simplicity of the control mechanism.
2.
water Reciprocator - SES
The two-stage pump presented for the water recip-
rocator was intended to reduce the lost work in a
bypassing system.
In this application, a venturi
flow sensor in the bypass line may be balanced
against one in the boiler delivery line so that
when bypass flow exceeds engine flow, the pump
would switch from parallel to series operation.
3.
organic Fluid Turbine - ALRC
3.1
Since the ideal switching points for the
organic fluid turbine are also a function of
expander speed, a speed actuator similar to
that described for the organic fluid recip-
rocator may be considered.
I-6

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ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
3.2
Throttle position'alone may also be used in
determining the switching point. Since, for
I

a given flow rate, the metering valve will
assume different positions dependent upon the
pressure differential, the switching point
will tend to be s~ifted with pressure.
The
benefit of this phenomenon is indicated in
the main body of this report where a shift
I
upward in flow with increasing pressure is
i
shown for the intersection of the series and
I
parallel efficiency curves at constant
expander speed.
whether or not the overshoots and undershoots that will
want to occur during transition will be a significant
factor will depend on the inertia of the expander and
the response of the speed variator.
An accumulator can
mitigate these effects.
It is also possible that the
I
switching can operate on the variable speed drive to
start the speed shift that ,the change in mode requires.
Deadband must be built into the switching mechanism to
avoid oscillation at the switching point.
130015
REV. 1165
I-7

-------
ENG. REPORT NO.
APTD-1357
DATE December 5, 1972
A hypothetical two-stage pumping system is shown sche-
matically in Figure 1-4, along with a simple 3-way pres-
sure actuated selector valve.
The main high pressure pumping elements are shown as
gear pumps.
A centrifugal inducer charges either one or
both high pressure stages, depending on the mode of
operation.
The accumulator may be used to supply fluid for high
flow transients and/or to dampen overshoots and under-
shoots during transition between the two modes of
operation.
The check valve is to prevent back flow to the first
element.
function.
In Figure 1-2, the switching includes this
All positive displacement pumps contain a
relief valve for protection.
In the Rankine cycle pump
system, this valve may perform double-duty by also
dumping flow at the high-speed, low-flow corner of the
operating envelope.
130015
REV. 1/65
1-8

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ENG. REPORT NO.
APTD-1357
DATE
December 5, 1972
The controlling parameters are not indicated in these
figures.
The selector valve reacts to a pressure sig-
nal which may be generated in many ways.
The benefits that accrue to the two-stage,
parallel, pumping system are:
series-
1.
The efficiency can: be maintained at higher
levels over the full pump speed range.
2.
The speed range of the variable speed drive
can be narrowed, permitting more efficient
operation of the d~ive.
3.
More of the engine operating envelope can
be obtained witho~t supplementary equipment.
The only apparent disadvantage is in 'the added system
complexity.
Furthermore, it remains to be seen whether
or not discontinuities will occur during transitions.
A more complete system analysis must be conducted to
ascertain the measures to ~e taken to resolve this
problem, if it exists.
130015
REV. 1/65
I-9

-------
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>
11
SERI ES ~3
Y'
1
ENGINE.
DR I VE
"
VARIABLE
SPEED
DRIVE
,
,
,
,
>
2
PARALLEL
SCHEMATI C
1
2
3
SUMP
SELECTOR VALVE
RE LI E F
VALVE
CHE CK
VALVE
()
ACCUMULATOR
CONTROL
PRESSURE
rICUPF T~4

-------