HYDROMATIC LIQUID BEARING ASSESSMENT

• Document Type: CREST
• Collection: NGA Records (Formerly NIMA)
• Document Number (FOIA) /ESDN (CREST): CIA-RDP78B04747A002800010001-0
• Release Decision: RIPPUB
• Original Classification: K
• Document Page Count: 76
• Document Creation Date: December 28, 2016
• Document Release Date: August 29, 2002
• Sequence Number: 1
• Publication Date: June 1, 1965
• Content Type: REPORT

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DECLASS REVIEW by NIMA/DOD
STATINTL
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HYDROMATIC LIQUID BEARING
RM-135-65
June 19 6 5
STATINTL
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STATINTL
submits this report in compliance with Item 3. 1
of the Development Objectives of
STATINTL
Approved:
Researc Manager
STAT
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within the bearing itself (Assignment STAT
Two approaches to the improvement of liquid bearings are feasible:
the first is to improve the efficiency of the bearing to require lower horse-
power input from a centrifugal pump, the second is to conceive a design in
which an external pump and plumbing are eliminated by integrating a pump
This assignment was issued to experimentally assess the state-
of-the-art in liquid bearing research, design, and development and, if
possible, improve existing concepts in preparation for a new generation of
photographic processors. Such factors as efficiency, economy, simplicity,
self-centering, elimination of guide flanges, and no necessity for format
changes to accommodate different film widths were to be considered. To
be given special attention were the advantages, if any, of slots over hole
jets as a film cushion support.
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This final report compiles data obtained on an exhaustive series
of tests on narrow liquid bearing prototype designs of single-slot, end-
feed bearings of varying cross section and material of construction, as
well as center-feed, self-centering bearings and end-feed tapered-slot
self-centering bearings. Certain hydrodynamic relationships were estab-
lished and a new concept of bearing design was evolved. To duplicate
the "crown effect" of belt roller, self-adjusting tracking, a reverse crown,
or "bow tie" pressure profile is necessary for hydraulic bearings. A bear-
ing was designed, constructed, and tested which exhibited self-aligning
features, imparted rotary motion to the film, and promised to be self-
adjusting to changing load conditions at constant flow. While it appeared
not to require guide flanges for operational stability, it did require format
changes for different film widths. Thus, not all of the design objectives
were achieved, but the advantages and shortcomings of the final design
are discussed in detail.
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1
INTRODUCTION
1-1
1.1
BEARING CONCEPT
1-1
1.2
PURPOSE AND OBJECTIVES
1-2
2
TECHNICAL DISCUSSION
2-1
2.1
EQUIPMENT AND INSTRUMENTATION
2-1
2.2
BEARING EXPERIMENTATION
2-1
2.2.1
Narrow Liquid Bearing Prototype
2-i
2.2.2
Liquid Bearing Slot Data
2-14
2.2.3
Self-Centering Liquid Bearings
2-27
2.2.4
Methacrylate End-Feed Self-
Centering Liquid Bearing
2-34
3
SUMMATION OF FINDINGS
3-1
3.1
NARROW LIQUID BEARINGS
3-1
3.2
END-FEED LIQUID BEARINGS
3-1
3.3
SELF-CENTERING LIQUID BEARINGS
3-2
3.3.1
Liquid Bearing Design Procedure
3-2
A
EQUIPMENT AND INSTRUMENTATION
A-1
B
PRESSURE GRADIENT CHARACTERISTICS
B-1
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FIGURE
ILLUSTRATIONS
PAGE
2-1
Liquid Bearing Test Rack
2-2
2-2
Rotameter Calibration Chart
2-3
2-3
Friction Factors for Straight, Clean, Round Pipes
2-4
2-4
Vernier Depth Gage
2-5
2-5
Narrow Prototype Liquid Bearing
2-6
2-6
Narrow Prototype Liquid Bearing Pressure Profile
(0.067" Slot)
2-7
2-7
Analysis of Pressure-Flow Relationship
2-11
2-8
Narrow Prototype Liquid Bearing with Cerrobend
Plenum and Plastic Wedge
2-13
2-9
Narrow Prototype Liquid Bearing with Wide Slot
2-15
2-10
Five Stainless-Steel Bearings - All Slots
0.063 x 9-1/2 Inches
2-18
2-11
Pressure Profile for 1.000" I.D. Circular
Stainless Bearing
2-19
2-12
Pressure Profile for 1.250" I.D. Circular
Stainless Bearing
2-20
2-13
Pressure Profile for 1.500" I.D. Circular
Stainless Bearing
2-21
2-14
Pressure Profile for 1.620" I.D. Circular
Stainless Bearing
2-22
2-15
Pressure Profile for 1.875" I.D. Circular
Stainless Bearing
2-23
2-16
Pressure vs. Flow for Experimental Bearings
2-24
2-17
Pressure Profile for 1.500" I.D. Circular
Copper Bearing
2-28
2-18
Double-Plenum Center-Feed Copper Bearing
2-31
2-19
Pressure Profile of Center-Feed Copper Bearing
2-32
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ILLUSTRATIONS (Continued)
2-20
Logarithmic Slot Self-Centering Liquid Bearing
2-33
2-21
Methacrylate Self-Centering Bearing
2-35
2-22
Cutaway Showing Construction of Methacrylate
Tapered-Slot, Self-Centering Bearing
2-36
2-23
Annular Velocity Versus Supported Weight -
9-1/2-Inch Film
2-40
2-24
Cushion Height at Constant Flow and Varying
Weight - 9-1/2-Inch Film
2-41
2-25
Annular and Transverse Areas at Different Weight
Loadings - 9-1/2-Inch Film
2-42
2-26
Pressure Profile for Tapered-Slot Liquid Bearing
9-1/2-Inch Width
2-45
2-27
Annular Velocity Versus Supported Weight -
6.6-Inch Film
2-49
2-28
Cushion Height at Constant Flow and Varying
Weight - 6.6-Inch Film
2-50
2-29
Annular and Transverse Areas at Different Weight
Loadings - 6.6-Inch Film
2-51
2-30
Pressure Profile for Tapered-Slot Bearing
6.6-Inch Width
2-52
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2-1 FLOWMETER CALIBRATION DATA AND REYNOLDS
NUMBER CALCULATION 2-8
2-2 PRESSURE PROFILE MEASUREMENT DATA FOR
NARROW PROTOTYPE LIQUID BEARINGS 2-9
2-3 WITH CERROBEND AND METHACRYLATE WEDGE
IN PLENUM 2-9
2-4 PRESSURE PROFILE MEASUREMENT DATA FOR
NARROW PROTOTYPE LIQUID BEARINGS 2-16
2-5 PRESSURE PROFILE MEASUREMENT DATA FOR
NARROW PROTOTYPE LIQUID BEARINGS 2-16
2-6 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-25
2-7 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-25
2-8 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-26
2-9 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-26
2-10 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-29
2-11 PRESSURE PROFILE MEASUREMENT DATA FOR
CIRCULAR CROSS-SECTION LIQUID BEARING 2-29
2-12 ANNULAR VELOCITY, CUSHION HEIGHT,
SUPPORTED WEIGHT 2-39
2-13 PRESSURE PROFILE MEASUREMENT DATA FOR
TAPERED-SLOT LIQUID BEARING 2-46
2-14 PRESSURE PROFILE MEASUREMENT DATA FOR
TAPERED-SLOT LIQUID BEARING 2-46
2-15 BEARING SLOT WIDTHS 2-47
2-16 ANNULAR VELOCITY, CUSHION HEIGHT,
SUPPORTED WEIGHT 2-53
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rR R - R R R --07
SECTION 1
INTRODUCTION
1. 1 BEARING CONCEPT
Prior to the innovation of the air and liquid bearing concept, all
commercial film processing units transported film on a series of rollers
(similar to the setup of a paper mill) or sprocket gears that matched the
perforations in standard types of perforated film. These conventional
machines use a preponderance of driven rollers, each of which must be
rotated at precisely the same speed as every other roller. If they are not,
one of two problems develops.
The first problem occurs when a variation of speed in the pressure
roller groups in either the wet or dry end of the processing line causes the
formation of a slack loop. This slack allows the film to slap against parts
of the processor or to cohere and damage itself by abrasion. The second
occurs when the film is suddenly shortened, which produces stretching,
riffling, or even film breakage.
With sprocket gears instead of rollers, the film can lose tracking
or its perforations can be torn. Any of these conditions, including the
normal slippage over a smooth roller, results in film damage, intolerable
in certain aerial surveillance and other irreplaceable original negative
films.
The liquid and air bearing principle, conceived by
was a significant contribution to the state-of-the-art. Its development has
advanced film processor design and has resulted in a new generation of
equipment. By providing a fluid cushion on each bearing in the wet end of
the machine and an air cushion in the drier section, the film could literally
be floated through the complete processing cycle contacting only its drive
STAT
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capstan and takeup spool. The supporting fluid cushion was created by
ejecting jets of liquid from within a cylindrical plenum. These jets, by
impinging on the film passing over the bearing, created a firm liquid layer
in the annular space. The air bearing is similar in principle.
Thus, in theory, the only frictional forces to which the film is
subjected, are the intermolecular drag coefficients and liquid viscosity
factors at the boundary interfaces. In practice, however, it proved nec-
essary to provide film guide flanges at either end to control the effluent.
Although these flanges were placed far enough apart to allow for the width
of film being used, there was still considerable edge friction due to er-
ratic film tracking along its multiple-bearing pathway in the processor.
One of the serendipities of the design concept proved to be this:
because the liquid creating the cushion in each stage of the processor
(developer, stop bath, fixer. etc.) was the chemical solution itself,
greater penetration of the emulsion was achieved, resulting in reduced
time of contact.
1.2 PURPOSE AND OBJECTIVES
In view of the state-of-the-art briefly outlined in the preceding
section, the objectives of this facet of the research program became clear.
Improve mechanical efficiency and reduce horsepower requirements while
increasing cushion stability. Eliminate guide flanges by designing a self-
centering bearing. Develop a bearing that, in ideal configuration, would
not require format changes to accommodate different widths of film. Es-
tablish design criteria so that bearing performance could be predicted
before fabrication.
STAT
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SECTION 2
TECHNICAL DISCUSSION
2: 1 EQUIPMENT AND INSTRUMENTATION
The details of assembly and adjunctive mensuration devices for
the liquid bearing test. rack (Figure 2-1) are presented in Appendix A. One
significant change was made in the test apparatus between the issuance
of the February Interim Report and this final paper. The closed-circuit re-
circulatory system illustrated introduced cyclic time fluctuations because
of the pump design and its proximity to the liquid bearing under test.
Rather than designing and building a pulse-smoothing device for insertion
in the line, the problem was largely eliminated by connecting the munici-
pal water faucet outlet directly to the flowmeter inlet. This meant, of
course, that the tank drain had to be opened during a test run to prevent
overflow and that the possibility of tempering the water temperature was
eliminated. However, the flow was greatly stabilized.
A new sensing pitot probe was built consisting of an 0.008-inch
inside-diameter steel capillary tube mounted in a 1/4-inch thin-wall tube.
The device was further improved by providing a tee at its outlet to prevent
having to bleed air bubbles from the long plastic hose connecting it to the
inclined manometer. This refinement greatly facilitated rapid measure-
ment of static pressures in the three slots during testing.
2.2 BEARING EXPERIMENTATION
2.2.1 Narrow Liquid Bearing Prototype
The first series of experiments was performed on an experimental
stainless-steel bearing (Figures 2-5, 2-6, and Table 2-2). Its overall
length was 13.9 inches and the inside diameter of its throat was 1.0 inch.
(Continued page 2-10)
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was varied. The nominal inside diameters were 1.000, 1.250, 1.500,
1.620, and 1.875 inches (Figure 2-10). The material was welded and
drawn tubing selected because it is less expensive than the seamless and
polished type and is normally stocked in raw stores STATINTL
These were "run-of-the-shop" jobs and no particular stress was placed
upon dressing the milled slots after machining.
Pressure profiles were measured on each bearing and then graphed
(Figures 2-11, 2-12, 2-13, 2-14, and 2-15, and Tables 2-5, 2-6, 2-7,
2-8, and 2-9). The construction material, the machine finish of the slot,
and the position of the seam relative to the slot appeared to be much more
critical parameters than was supposed. When the empirical data obtained
on all bearings were grouped on one graph, the differences became appar-
ent (Figure 2-16).
The most and the least satisfactory bearings from the standpoint
of economy of fluid flow were the two narrow prototypes discussed in Sec-
tion 2.2. 1. However, since the effective area available for the cushion
support of film was only 47 and 42 percent respectively for these bearings,
the results should not be misinterpreted. The five experimental stainless-
steel bearings were grouped rather closely and differed mainly in their
effective support areas. The fact that the curve for the 1.620 inch inside
diameter bearing falls to the left of those for the 1.500 and the 1.875 inch
inside diameter bearings supports the statement concerning the critical
nature of some of the parameters.
The 1.500 inch inside diameter copper bearing discussed in Sub-
section 2.2.3 following, proved to be the most satisfactory compromise
among the parameters.
(Continued page 2-27)
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6.75 PSI
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INSIDE DIAMETER= 1
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 Approved For Release 2002/09/03 : CIA-RDP78BO4747AO02800010001-0
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SLOT WIDTH :.063"
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2.2.3 Self-Centering Liquid Bearings
In the list of experimental objectives, one important aim was to
produce a liquid or air bearing that would tend to keep the film centered
while it travelled through the processor, regardless of minor bearing mis-
aligmments. In the ideal configuration embodying this principle, the edge
guides would be eliminated.
To attain this objective, a simple, single-slot bearing was built
from smooth, polished copper. Its length was 20-1/4 inches; the inside
diameter was 1.500 inches ?.005 inch, and the slot was 9-1/2 inches by
0.063 inch. The pressure profile was carefully measured (Figure 2-17)
and Table 2-10) and the bearing was modified as discussed below.
Many years ago most machine tools were belt-driven by a series
of overhead pulleys connected to a central power source. These pulleys
were cylindrical, with a slight crown to keep the belts centered. Apply-
ing this principle directly to the liquid bearing problem, a unit was prod-
uced whose maximum liquid pressure was at the center. This was done by
utilizing the parabolic principle previously discovered with the narrow
bearings (see Figure 2-7). By selecting a tube of such size that is inter-
nal cross-sectional area was equal to the annular area between its outside
diameter and the inside diameter of the main bearing tube, the objective
was accomplished. When the smaller tube was mounted on a solid bulk-
head located midway on the slot and water was injected in one end, fluid
flowing in the annular area formed a parabola toward the center, while
fluid flowing through the inner pipe was forced to reverse its direction at
the downstream end, forming a second parabola which met the first one at
the center. The combined flow created a high-pressure area at the center
of the slot and its waterfall pattern was extremely symmetrical.
STAT
(Continued page 2 -3 0)
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