Removable strain gauge fixture and method for measuring accumulated strain in a material

The invention encompasses a removable strain gauge fixture, and a method for measuring accumulated stress in a structural component, such as a railroad rail. The strain gauge fixture generally comprises first and second side pieces connected by a strain concentrating bar of reduced cross-section, an electronic strain sensor mounted on the bar, and first and second tapered pins extending from the front faces of each of the side pieces. The tapered pins transmit accumulated strain from the component being measured to the strain focusing bar when the pins are inserted into mating holes in the component. The method of the invention generally comprises the steps of providing a pair of holes in the component mateable with the tapered pins of the strain gauge fixture, inserting the tapered pins into the holes of the material in order to transfer accumulated strain in the material to the strain concentrating bar, taking a first strain measurement via the strain sensor on the bar, removing the tapered pins from the material, and taking a second strain reading from the strain sensor.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
This invention relates to a removable strain gauge fixture, and a method 
for measuring the accumulated strain in a material, such as the rail of a 
railroad track. 
2. Description of the Prior Art 
Strain gauges for measuring strain in structural components are known in 
the prior art. Typically, such strain gauges generally comprise a strain 
gauge carrier having an electronic strain sensor mounted thereon. In use, 
the strain gauge carrier is usually welded or otherwise permanently 
affixed to the component being measured. A first strain reading is taken 
when the component is in a strain-free state. Next, the component is 
subjected to strain, and a second strain reading is taken. The strain, and 
therefore the stress, is computed by subtracting the values of the two 
readings, and multiplying the result by an appropriate constant. 
While prior art strain gauges are capable of rendering accurate strain 
measurements in certain applications, such gauges may provide unreliable 
and inaccurate results when used in a hostile environment over a long 
period of time. Specifically, such gauges have been known to fail a few 
years after being attached to a railroad rail, where weather and vibration 
take a daily toll on both the gauge carrier as well as the delicate 
electronic strain sensor. Such gauges are not designed to be removed from 
and reattached to their respective rails, and therefore must remain with 
the rail and its environment throughout the life of the test. 
Clearly, a need exists for a strain gauge and a strain measurement method 
in which the gauge fixture is easily attachable and removable from the 
component being measured and hence capable of being stored in an ideal 
environment when not in use, and which is capable of transferring and 
measuring accumulated strain when attached onto the component. Ideally, 
such a strain gauge fixture should be simple and inexpensive to fabricate, 
and the method of using it should be easy to carry out and capable of 
rendering accurate, reliable strain measurements. 
SUMMARY OF THE INVENTION 
The invention relates to a removable strain gauge fixture, and a method for 
measuring accumulated strain in a material. The removable strain gauge 
fixture generally comprises a strain gauge carrier including two side 
pieces connected by a bar of cross-sectional area smaller than that of the 
side pieces for concentrating strain transmitted to the side pieces, at 
least one electronic strain sensor mounted on the strain-concentrating 
bar, and first and second tapered pins extending from the front faces of 
the first and second side pieces, respectively, for transmitting 
accumulated strain in a material to the strain-concentrating bar. The 
strain gauge carrier further includes a pair of longitudinally extendable 
side braces on opposite sides of the side members to protect the centrally 
disposed, strain-concentrating bar of reduced cross-sectional area from 
spurious strains during the attachment or removal of the gauge from the 
material being measured, thereby enhancing the accuracy of the 
measurements, and minimizing the danger of damage to the fixture during 
attachment to and removal from the component. 
The method of the invention generally comprises the steps of providing a 
pair of holes in the material being measured which are mateable with the 
tapered pins of the removable strain gauge, inserting the pins of the 
strain gauge fixture into the holes of the material, taking a strain 
reading from the strain gauge fixture while the gauge fixture is thus 
inserted, removing the strain gauge fixture, and taking a second reading 
from the strain gauge after the pins have been removed from the holes in 
the material. 
The strain gauge carrier may be made from the same material as the material 
being measured, and the method of the invention may further include the 
step of waiting for the strain-concentrating bar to achieve thermal 
equilibrium with the material being measured when the tapered pins are 
inserted into the mating holes of the material. The method of the 
invention may also include conditioning the mating holes in the material 
prior to taking any strain gauge readings by forcefully inserting the pins 
into the mating holes in order to level any high spots in the surfaces 
defining the holes. 
Finally, the method of the invention may further include the step of 
removing the strain gauge fixture by providing a pair of threaded studs on 
each of the side pieces opposite its respective tapered pin, providing a 
U-bar structure having a pair of apertures registrable with the ends of 
the threaded studs, placing the U-bar over the studs so that the ends of 
the studs are in registry and extend through the apertures of the bar, and 
gradually withdrawing the strain gauge fixture from the material being 
measured by screwing nuts onto the ends of the threaded studs, and 
alternately tightening these nuts in small increments.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
With reference now to FIGS. 1 and 2, wherein like numerals designate like 
parts of the invention, the strain gauge fixture 1 of the invention 
generally comprises a gauge carrier 5 which includes two symmetrical side 
pieces 7a, 7b centrally connected together by means of a 
strain-concentrating bar 9 having a smaller cross-section than side pieces 
7a, 7b. Bar 9 carries a pair of electronic strain sensors 40, 42 on its 
front and back faces, respectively. Preferably, bar 9 is about 1" long, 
1/4" wide, and about 1/16" thick, while side pieces 7a, 7b are about 13/8" 
square as shown, and about 1/2" thick. Each of the side pieces 7a, 7b 
includes an orthogonally disposed, tapered pin 11a, 11b, extending from 
its front face. Generally speaking, the strain gauge fixture 1 of the 
invention functions by transmitting and concentrating accumulated strain 
in the material being measured to bar 9. Specifically, accumulated stress 
is transmitted from the material to the tapered pins 11a, 11 b and thence 
to bar 9 through the relatively heavy side pieces 7a, 7b. Since bar 9 has 
the smallest cross-section and therefore the smallest spring constant of 
any part of the gauge carrier 5, the bulk of any strain exerted on the 
carrier 5 is concentrated along the relatively small cross-section of bar 
9, where it is measured by strain sensors 40, 42. 
The pins 11a, 11b are preferably mounted in the side pieces 7a, 7b by 
completely inserting the shank of each pin through a bore (not shown) in 
its respective side piece, and welding the head and shoulder of each pin 
into place via a precision welding fixture (also not shown) so that the 
centers of the pins 11a, 11b vary no more than .+-.0.0005 inch from a 
standardized distance. Such precision welding of the pins 11a, 11b in 
proper position on side pieces 7a, 7b allows them to be inserted into a 
pair of mating holes 4a, 4b in a material such as the railroad web shown 
in FIG. 1 without generating spurious or misleading strain on bar 9. 
Turning now to the structure of the pins 11a, 11b, each includes a tapered 
shank portion 13a, 13b, respectively. In the preferred embodiment, 
commercially available 23/4" tapered steel pins are used to form pins 11a, 
11b. Such pins have a tapered shank portion approximately 13/16" long, and 
should preferably have a No. 2 Morse taper. Each of the tapered pins 11a, 
11b terminates in a threaded end 15a, 15b. The threaded ends 15a, 15b of 
the pins allow them to be temporarily secured to a material such as the 
rail web illustrated via washers and nuts 17a, 18a and 17b, 18b, as shown. 
More importantly, the threaded ends 15a, 15b, in conjunction with the 
aforementioned nuts and washers, allow the pins 11a, 11b of gauge carrier 
5 to be conveniently pulled through holes 4a, 4b for either conditioning 
the holes or taking a measurement of the accumulated strain present in the 
material, as will be more specifically explained hereinafter. 
The gauge carrier 5 further includes a top side brace 21 and a bottom side 
brace 23 for protecting the bar 9 of reduced cross-section from spurious 
strain due to warping or bending when the strain gauge fixture 1 is being 
attached to or removed from the web of rail 3. As is best shown in FIG. 2, 
top side brace 21 includes a pair of serially aligned cylindrical members 
25a, 25b which are joined by a pin 29 which is inserted through a 
centrally disposed bore (not shown) present in each of the cylinders. 
Analogously, side brace 23 includes a pair of serially aligned cylindrical 
members 31a, 31b joined by a pin 35 which is likewise inserted through a 
centrally disposed bore present in each. In each of the side braces 21, 23 
the pin 29, 35 has a slightly elevated shoulder (not shown) just under its 
head, which causes the pin to frictionally engage the cylinders 25a, 31a 
which house the upper portions of these pins when the pins are tapped into 
place. By contrast, the pins 29, 35 do not frictionally engage the 
cylinders 25b, 31b which house the lower portions of the pins. Hence, top 
side brace 21 and bottom side brace 23 are slidably movable along the 
longitudinal axis of the gauge carrier 5, and accordingly, will not 
interfere with the expansion or contraction of bar 9 when strain is 
applied to the side pieces 7a, 7b of carrier 5 through pins 11a, 11b. By 
protecting bar 9 from spurious transfer of strain during the attachment 
and removal of gauge carrier 5 to the material being measured, the side 
braces 21, 23 allow the use of a smaller cross-section in bar 9 than would 
be necessary if such braces were not present. This use of a reduced 
cross-section in bar 9 increases the sensitivity and accuracy of the gauge 
fixture 1, and reduces the amount of strain applied to the pins 11a, 11b 
and side pieces 7a, 7b of the gauge carrier 5 when measurements are taken. 
The gauge carrier 5 preferably should be completely fabricated from the 
same material as the component being tested. In this way, the gauge 
carrier 5 and the material being tested will have the same thermal 
properties, thereby obviating the use of temperature data when computing 
strain, and hence force, from the readings obtained from the strain 
sensors 40, 42. 
Strain gauge fixture 1 also includes an electronic strain sensor 40, 42 on 
the front and back faces of the strain concentrating bar 9, as shown. In 
the preferred embodiment, sensors 40, 42 each comprise a rosette having 
two elements 44a, 44b and 46a, 46b, respectively. The two elements of each 
of the rosettes are oriented 90.degree. to one another. Rosette elements 
44a, 46a measure longitudinal strain in bar 9, while rosette elements 
44b, 46b measure transverse strain in bar 9. The dual element rosettes may 
be of conventional, foil-type construction, and form no part of the 
instant invention. In the preferred embodiment, dual element rosettes 
(Model Nos. WK-06-125TA-350) manufactured and distributed by 
Micro-Measurements Companying of Raleigh, N.C. are mounted on the back and 
front faces of bar 9. The rosette elements 44a, 44b and 46a, 46b measure 
the strain in bar 9 by varying their resistances as a function of the 
strain present in bar 9, as will be described in more detail hereinafter. 
With reference now to FIGS. 2 and 3, two wires extend from each element 
44a, 44b and 46a, 46b of the rosettes forming sensors 40 and 42. In sensor 
40, the wires extending from each of the rosette elements 44a, 44b are 
connected to electrical terminals 50a, 50b, respectively. Analogously, in 
sensor 42, the wires extending from each of the rosette elements 46a, 46b 
are connected to terminals 54a, 54b, respectively. Terminals 50a, 50b and 
54a, 54b may be any one of a number of commercially available terminal 
boards or plug-in modules. Terminals 50a, 50b and 54a, 54b are in turn 
connected to a coaxial, multi-element input cable 56 of a commercially 
available strain gauge readout unit 58. In the preferred embodiment, the 
readout used is a Model No. 120C manufactured by the nationally known BLK 
Corporation. The coaxial, multi-element cable 56 is attached to the strain 
gauge carrier 5 via a stress relieving cable mounting assembly 59. 
Assembly 59 includes a circular cable clamp 61 of conventional 
construction, which is attached to a right-angle bracket 63. Bracket 63 is 
in turn attached to side piece 7b through mounting bolt 65 and nut 67, as 
shown. 
The electronic circuitry of the strain gauge fixture 1 is schematically 
illustrated in FIG. 4. As shown in the schematic, the outputs of the 
rosette elements 44a, 44b and 46a, 46b are arranged in a Wheatstone bridge 
configuration. Specifically, the outputs of the longitudinal rosette 
elements 44a, 46a are added, as are the outputs of the transverse rosette 
elements 44b, 46b. The sum of the transverse rosette elements 44b, 46b is 
subtracted from the sum of the longitudinal rosette elements 44a, 46a. 
There are three principal advantages associated with this Wheatstone bridge 
configuration. First, this bridge configuration amplifies the outputs of 
the rosette elements by a factor of 2.6. Longitudinally induced strain in 
bar 9 is multiplied by a factor of 2, since the longitudinal rosette 
elements 44a, 46a experience the same strain and their outputs are summed 
in the electrical bridge. In the transverse direction, the strain 
experienced by transverse rosette elements 44b, 46b is opposite in sign 
(or direction), and proportional to that in the longitudinal direction by 
a factor of 0.3 (via Poissons Ratio). Since the transverse oriented strain 
gauges are likewise added in the electrical bridge, the sum of the two 
outputs is 0.6. In the bridge, however, transverse outputs are subtracted 
from the longitudinal outputs so that the algebraeic sum of the outputs of 
rosette elements 44a, 44b and 46a, 46b is 2.6, i.e., 
[(2.times.1)-(2.times.-0.3)=2.6]. Further, this bridge configuration also 
corrects for spurious bendings of bar 9 by the fact that in a bending 
mode, one side of the bar 9 is in compression and the opposite side in 
tension by equal amounts. Since the outputs from the two rosette elements 
of sensor 40 in compression are equal to the outputs of the two rosette 
elements of sensor 42 in tension, the resultant is zero. Finally, the 
bridge configuration compensates for thermal expansion. Metals expand 
equally in all directions; under these conditions, thermally induced 
strain in the longitudinal directions equals the strain in the transverse 
direction. In the Wheatstone bridge, the longitudinal strain outputs are 
substracted from the transverse strain gauge outputs. The resultant of the 
output subtraction is zero for uniform expansion, thus making the 
configuration self-correcting for changes in temperature. 
Turning now to the preferred method of the invention, and FIGS. 5 through 
7, there are six basic steps in measuring accumulated strain in a material 
with strain gauge fixture 1. First, as illustrated in FIG. 5, a pair of 
tapered, mating holes 4a, 4b is drilled and reamed in the material 3 to be 
measured, which in this case is the web of a railroad rail 3. Second, as 
shown in FIG. 6, the surfaces defining the holes 4a, 4b are conditioned to 
remove high spots by forcefully and uniformly pulling the pins through the 
holes 4a, 4b in the rail web by means of a gauge-attaching assembly 90. 
Third, the tapered pins 11a, 11b of the strain gauge fixture 1 of the 
invention are fitted to the pair of holes 4a, 4b to make sure that the 
distance between the centers of the holes and the pins are within 
tolerance levels. Fourth, after the rail 3 has undergone strain, the 
strain gauge fixture 1 is temporarily mounted in the material by again 
pulling the pins 11a, 11b of the strain gauge fixture 1 forcefully and 
uniformly through the holes 4a, 4b via gauge fixture attaching assembly 
90. A strain reading is taken after the gauge carrier 5 and rail 3 have 
had an opportunity to establish thermal equilibrium with one another. 
Fifth, as shown in FIG. 7, the gauge fixture 1 is removed from the 
material 3 by means of a removal assembly 100 including a U-bar 102, studs 
101a, 101b and nuts 106a, 106b. Sixth, a second strain reading is taken 
from the strain gauge fixture 1 shortly after it is completely removed 
from the holes 4a, 4b of the web of rail 3. These first and second strain 
readings may be used to compute the accumulated strain in the material 3, 
and hence the stress. 
Turning again to FIG. 5, and a more detailed description of the preferred 
method of the invention, a pair of tapered holes mateable with tapered 
pins 11a, 11b is first drilled and reamed into the material being 
measured. In FIG. 5, this material corresponds to the web of railroad rail 
3. The distance between the centers of the holes drilled and the centers 
of the tapered pins 11a, 11b should be within .+-.0.0005 inch in order to 
avoid spurious readings on the strain gauge fixture 1. Such holes are 
preferably drilled and reamed by means of a Model SM-1-40 precision rail 
drill manufactured by Scientific Models, Inc. of Cambridge, Mass., which 
is slideably mounted on the guide rods 89a, 89b of jig frame 72 as shown. 
The jig frame 72 guides the bit or reamer 71 through a bit guide 73 on the 
web of the rail 3. Front feet 74a, 74b of jig frame 72 are capable of 
securely clamping on the foot of the rail 3 as shown. In the jig frame 
illustrated, U-clamp members 76a, 76b are used to clamp front feet onto 
the base of the rail 3. For further securing and positioning the bit guide 
73 on the web of rail 4, the jig 72 preferably includes a pair of 
vertically adjustable rear legs 78a, 78b and clamps 84a, 84b. Rear legs 
78a, 78b are formed from threaded shafts 80a, 80b crowned by handles 82a, 
82b as shown. Handles 82a, 82b may be adjusted so that the drill bit guide 
73 is orthogonally disposed to the surface of the web of rail 3, thereby 
insuring proper penetration of bit or reamer 71. The pair of manually 
operable securing clamps 84a, 84b are tightened on either side of a 
railroad tie in order to secure the jig frame 72 in proper position once 
the threaded shafts 80a, 80b of rear legs 78a, 78b are adjusted. Jig frame 
72 also includes a spindle 86 for rotating a threaded shaft 88 connected 
to the precision drilling unit 70, so that the unit 70 may be accurately 
and easily moved along guide rods 89a, 89b. In the preferred method of the 
invention, a first hole is drilled and reamed via precision drilling unit 
70. The chuck (not shown) of the drill is then pivoted over a proper 
distance, and the second hole is drilled and reamed. 
FIG. 6 illustrates the hole conditioning, gauge fixture selection, and 
gauge fixture attachment steps of the method of the invention. After a 
pair of mating holes 4a, 4b has been provided by the precision drilling 
unit 70 and jig frame 72 as previously described, the holes 4a, 4b are 
conditioned in order to remove any high spots on the surfaces defining 
these holes by means of a gauge fixture attaching assembly 90. In this 
step of the invention, a dry lubricant such as moly-disulfide is first 
applied to the surfaces of both of the pins 11a, 11b and holes 4a, 4b. The 
pins 11a, 11b are then carefully inserted into the mating holes 4a, 4b 
until threaded ends 15a, 15b extend through the other side of the web of 
rail 3 as shown. A pair of self-leveling nuts 96a, 96b are evenly screwed 
down on the protruding, threaded ends 15a, 15b of the pins 11a, 11b in the 
position shown. A bolt 98 is threaded through a centrally disposed, 
threaded aperture in plate 92, which is shown in FIG. 6 as nut 99 welded 
onto plate 92. When bolt 98 is turned counterclockwise with a torque of 
approximately 50 pound-feet, any high points in the surfaces defining the 
tapered holes 4a, 4b are flattened. Rail steel has a yield strength of 
about 72,000 psi, and the force along the axis of the pins required to 
generate that pressure is approximately 100,000 pounds. The inventors have 
found that the recommended torque of 50 pound-feet, when used in 
connection with a tapered pin having a Morse taper rating of 2, is 
sufficient to level any high points on the surfaces defining the holes. 
Such conditioning enhances the accuracy of the readings given by gauge 
fixture 1. 
After the holes are conditioned, the gauge fixture 1 should be removed via 
the U-bar removal assembly 100 illustrated in FIG. 7. In the first step of 
this removal procedure, a pair of studs 101a, 101b are threaded into the 
removal nuts 19a, 19b located on the back faces of side pieces 7a, 7b, 
respectively. Next, a U-bar 102 having a pair of apertures 104a, 104b 
registrable with the ends of the studs 101a, 101b is placed over the gauge 
fixture 1 so that the stud heads extend through the face of the U-bar 102, 
as shown. Finally, a nut and washer 105a, 106a and 105b, 106b is threaded 
over each of the heads of the studs 101a, 101b in the manner illustrated. 
The two nuts 106a, 106b are alternately tightened in small steps of no 
more than 5 pound-feet to avoid either damaging the gauge carrier 5, or 
creating a spurious strain in bar 9. (In FIG. 7, only the parts 101a, 
104a, 105a and 106a are expressly shown; however, as the assembly is 
perfectly symmetrical, parts 101b, 104b, 105b and 106b are identical to 
their "a" counterparts). 
In the next step of the method of the invention, a proper strain gauge 
fixture is selected for holes 4a, 4b to insure that the holes mate with 
pins 11a, 11b of the gauge fixture 1 to within a tolerance of .+-.0.0005 
inch. This step is performed by first cleaning the inner hole surfaces 
with trichlorethylene or gasoline, and then applying a dry lubricant, such 
as moly-disulfide to the pins 11a, 11b and hole surfaces. This gauge 
fixture 1 is next connected to the readout unit 58, and a reading is taken 
of the gauge in a stress-free state. The pins 11a, 11b of the gauge 
fixture 1 are then evenly inserted into the mating holes in the web of 
rail 3 by hand. Care should be taken to evenly insert pins 11a, 11b into 
holes 4a, 4b, and not in a cocked position. Next, after the threaded end 
portions 15a, 15b of the pins extend out of the back of the web of rail 3, 
the gauge fixture attaching assembly 90 should be used to pull the tapered 
pins into position on the rail 4 by wringing bolt 98 in increments of 5 
pound-feet up to a torque of 50 pound-feet. The strain readings of the 
gauge fixture 1 should be recorded with every 5 pound-feet increment of 
torque. If the difference between the strain-free reading of the gauge 
fixture 1 in any of the 5 pound-feet readings exceeds .+-.1200 
microstrains, the fitting procedure should be aborted and a different 
gauge fixture 1 selected for the fitting. On the other hand, if the 
difference between these readings never exceeds .+-.1200 microstrains at 
any point in the procedure, the gauge fixture 1 properly mates with the 
holes 4a, 4b. After the fitting, the gauge fixture 1 should be removed 
with the U-bar assembly 100 as previously described. 
When it is desired to measure the accumulated strain in a material such as 
rail 3, holes 4a, 4b are again cleaned with trichlorethylene or gasoline, 
and a dry lubricant such as moly-disulfide is again applied to the 
surfaces of the holes 4a, 4b and the pins 11a, 11b of the fitted gauge 
fixture 1. The gauge fixture 1 is again connected to cable 56 of readout 
unit 58, and a strain-free readout is taken. If the strain-free readout is 
not within .+-.25 microstrains of the strain-free calibration value of the 
gauge fixture 1, the electrical connections of the gauge fixture 1 should 
be checked for possible damage (i.e., terminals 50a, 50b and 54a, 54b). If 
the unsatisfactory reading cannot be corrected by checking the electrical 
connections of the gauge fixture 1, the procedure should be aborted. 
However, if there is no such unsatisfactory reading, or if the reading is 
corrected, the pins 11a, 11b of the gauge fixture 1 should be hand-placed 
in the mating holes 4a, 4b of the web of the rail 3, so that the threaded 
ends 15a, 15b of the pins 11a, 11b extend through the rail web. Next, the 
pins 11a, 11b of the gauge fixture 1 should be pulled through the web of 
the rail 3 via gauge fixture attaching assembly 90 in a similar manner as 
described in the hole conditioning step, with the exception that a maximum 
torque of only 30 pound-feet should be initially applied to bolt 98. Next, 
the bolt 98 should be loosened, and retightened up to 40 pound-feet. 
Finally, the bolt 98 should be loosened again, and retightened to 50 
pound-feet. After the bolt 98 of the gauge fixture attaching assembly 90 
is loosened (after being tightened to 50 pound-feet), gauge fixture 
attaching assembly 90 should be carefully removed. Next, temperature 
gauges (not shown) should be attached to both the gauge carrier 5 and the 
web of rail 3. When the temperature gauges indicate that the gauge carrier 
5 and web of rail 3 have reached the same temperature, a first strain 
reading should be recorded. Finally, the U-bar removal assembly 100 should 
be used to remove the gauge fixture 1 from the rail 3 in the manner 
heretofore described, and a second strain reading should be taken before 
the gauge carrier 5 has an opportunity to significantly change its 
temperature. 
After all of the previously mentioned readings have been taken and 
recorded, the accumulated strain, and therefore stress, in rail 3 is 
computed via the following formula, where: 
Sf=the strain measured with the gauge fixture 1 when the gauge is attached 
to the rail 4 in a stress-free state, and is in thermal equilibrium (as it 
should be during the gauge-fitting step); 
Sfg=the strain measured with the gauge fixture 1 immediately after it has 
been removed from the rail 4 after the gauge fixture fitting step, and is 
at the same temperature as the strain-free rail; 
S=the strain measured with the gauge fixture 1 when the gauge fixture is 
attached to the rail 4 in a stressed state, and is at the same temperature 
as the rail, and 
Sgs=the strain measured with the gauge fixture 1 immediately after it has 
been removed from the stressed rail 4, and is at the same temperature as 
the stressed rail. 
The net strain Sn measured by the gauge fixture 1 is: 
EQU (Sfg-Sf)-(Sgs-Ss)=Sn 
Consequently, the force fn measured by the gauge fixture 1 is: 
EQU Sn.times.C.sub.1 =fn 
where C.sub.1 is the calibration factor for each gauge fixture 1. 
Theoretically, the strain gauge fixture 1 is oriented and electrically 
connected to compensate for thermal expansion and contraction, and under 
ideal conditions, Sfg and Sgs would have the same value at any time the 
reading is taken. But for tests that are performed over long periods of 
time, the intervals between the Sfg and Sgs measurements could be months 
apart, and the value of the readings could change with time, due to aging 
or other affects which cause long-term drift. 
It should be noted that, in order to enhance the accuracy of the readings, 
holes 4a, 4b may be plugged with cork or rubber (not shown) in order to 
keep out grit and dust, and to discourage formation of rust on the 
surfaces defining the holes. 
Although the present invention has been described with reference to a 
preferred embodiment, it should be understood that the invention is not 
limited to the details thereof. A number of possible substitutions and 
modifications have been suggested in the foregoing detailed description, 
and others will occur to those of ordinary skill in the art. All such 
substitutions and modifications are intended to fall within the scope of 
the invention as defined in the appended claims.