2002-01-0797
TRANSCRIPT
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400 Commonwealth Drive, Warrendale, PA 15096-0001 U.S.A. Tel: (724) 776-4841 Fax: (724) 776-5760
SAE TECHNICALPAPER SERIES 2002-01-0797
Component Testing and Materials Properties
of Ductile Iron Brake Anchors
Alan P. Druschitz, Nathan J. Sochor and Brandon ReneauIntermet Corporation
SAE 2002 World CongressDetroit, Michigan
March 4-7, 2002
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2002-01-0797
Component Testing and Materials Properties of Ductile
Iron Brake Anchors
Alan P. Druschitz, Nathan J. Sochor and Brandon Reneau
Intermet Corporation
Copyright 2002 Society of Automotive Engineers, Inc.
ABSTRACT
During product development and production, product
testing is often desirable to improve design robustness
and verify consistent product performance. However,
product testing is very complicated, requires highly
specialized and trained personnel and utilizes expensive,dedicated equipment and facilities.
This paper describes two brake anchor component tests
(pull and impact) and the use of strain gaged components
to determine the characteristics of the component during
loading. Data for two brake anchor designs are presented
and the component properties are then correlated with
material properties and design. The combined effect of
material properties and component design on performance
is demonstrated. The data also demonstrates that
apparently identical tests on different component designs
can lead to misleading conclusions.
BACKGROUND
Product testing has been and will continue to be a crucial
part of the product development cycle since current math
models cannot fully take into account variable material
properties and cannot fully account for all loading
conditions that might be encountered in service. For
example, castings cool at different rates in different
locations and therefore always have varying mechanical
properties. Also, the loading conditions in the foundry or
machining line often exceed those encountered in service.
Since a math model can only calculate the effect of the
loads input into the model and the material properties
assigned to the component, unforeseen loading conditions
and unforeseen material property variations may produce
early failures.
For this study, a relatively simple component (brake
anchor) was selected to demonstrate how design and
material properties interact. For this demonstration, a
variety of tests were performed: 1) one brake anchor
design was tested in two different loading conditions (pull
and impact) and 2) two brake anchor designs were tested
in numerous material conditions (as-cast and various heat
treatments). This type of data is needed by the design
engineer when specifying material requirements
developing new components and developing component
test specifications.
COMPONENT DESCRIPTION, TEST
METHODS AND MATERIAL PROPERTIES
Two similar brake anchors designed by differen
companies and produced at the INTERMET Havana
Foundry were selected for this study. The differences
between these brake anchors were both obvious and not
so obvious. The obvious difference was the shape of the
thin tie bar. In Figure 1a, the tie bar of brake anchor A
looks much thinner than the tie bar of brake anchor B.
However, when the brake anchors are inclined, Figure 1b
the tie bars appear nearly identical. Actually, the tie bar
of brake anchor A was thicker and had a well roundedcross section whereas the tie bar of brake anchor B had
two flat surfaces incorporated into the tie bar for fast brake
pad changes, which significantly reduced the cross
section thickness, and formed relatively sharp corners.
The cross sections of the two brake anchor designs are
shown in Figure 2. The not so obvious difference was the
microstructure and chemistry of the material. Basically,
both brake anchor castings had similar microstructures
with brake anchor A having slightly more pearlite, Figures
3a and b. However, brake anchor design B was prone to
carbide formation at the edges of the tie bar due to sharp
corners that cooled rapidly, Figure 4. Because of this
design problem, higher silicon content was used to
produce brake anchor B, which resulted in lower pearlite
content at approximately the same hardness.
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Figure 1a. Straight-on view of brake anchor designs A and B.
Figure 1b. Inclined view of brake anchor designs A and B.
Two tests were selected for this study: pull and impact.
The pull test simulated the component loading on the
vehicle and the impact test simulated the worst case
handling condition that might be encountered in the
foundry or machine shop.
The pull test loads the brake anchor under conditions
similar to those seen in service. Here, a rigid fixture,
which would be the steering knuckle on a vehicle, was
attached to the lower, moveable ram on a hydraulic load
frame, the brake anchor was bolted to the fixture, the load
arm swung into position (this arm was connected to the
upper, fixed ram) and the brake anchor pulled to failure,
Figures 5a and b. In this test, the load was applied off-
center and the brake anchor rotated under the attachment
bolts. This produced a bending stress. Since the brake
anchor rotated under the bolt, the measured load was a
function of bolt torque. Production bolts, a specified
torque value and a specified thread locking adhesive set
up time were used. During the pull test, the thin tie bar
broke followed by failure of the thicker section and
sometimes the upper bolt. Looking more closely at the
sample orientation, a clear difference in the location of a
reduced section or pocket on the thicker section of the
driver side and passenger side castings is evident. The
importance of this difference will be discussed later.
Figure 2. Cross sections through the tie bar of brake anchor designsA (left) and B (right). A mm scale is on the bottom of the photograph
Figure 3a. Typical microstructure in the tie bar region of brake anchordesign A showing well formed graphite nodules in a matrix of ~20%ferrite and 80% pearlite.
1 mm
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Figure 3b. Typical microstructure in the tie bar region of brake anchordesign B showing well formed graphite nodules in a matrix of ~30%ferrite and 70% pearlite.
Figure 4. Carbides in tie bar of brake anchor design B.
The impact test was developed to simulate the worst case
loading condition that might occur in the production
foundry or machine shop. In this test, the brake anchor
was attached to a rigid fixture and a hydraulic ram
punched the thin tie bar at a velocity of 254 mm per
second, Figure 6. The load as a function of ram
displacement was measured and recorded. From this
data, the energy required to initiate a crack (area under
the curve up to the point of maximum load) and the tota
energy absorbed (area under the entire curve) was
calculated by numerical integration. These values can be
compared to various loading events in the foundry and
machine shop to determine if damage might occur. A
typical load versus displacement curve is shown in Figure
7. The orientation of the tie bar cross section was critica
in this test and thus, an additional angled support was
necessary to allow the two different components to betested under identical loading conditions.
Figure 5a. Typical pull test set-up.
Figure 5b. Close-up of pull test set-up showing dial gages used fordisplacement measurement.
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Figure 6. Typical impact test set-up.
Figure 7. Typical load versus displacement curve for the impact test.
The casting microstructure and chemistry, which
determined material properties, had a significant effect on
component performance. To vary the properties in a
controlled manner, samples of both casting designs were
sub-critically annealed (softened), normalized (hardened)
or normalized and tempered. The microstructures were
characterized using a fully automated Clemex image
analyzer. All castings had better than 90% nodularity
The tensile properties where determined from 6.3 mm
diameter, 25.4 mm gage length tensile bars cut fromcastings. Five tensile bars of each condition were tested
in accordance with ASTM E8 and the results averaged.
The material properties of the as-cast and heat treated
castings are listed in Table I.
RESULTS AND DISCUSSION
PULL TEST. The orientation of the specimen in the pul
test fixture resulted in a difference in the measured load a
failure of as much as 36%. The reason for this difference
was the location of the fracture. Lower load at failure
values were measured when fracture occurred through the
thin pocket on the thicker section. Figures 8a and b and9a and b show the pull test specimens before and after
testing. This was not an unexpected result since the
amount of bending caused by rotation of the component
during loading was greater near the load application point
(upper half of the casting). An unforeseen consequence o
this loading variation was rapid deterioration of the fixture
for the orientation shown in Figures 9a and b. Due to the
significantly higher load, the bolt hole tended to elongate
with a subsequent loss of clamping ability, Figure 10. As
the amount of bolt hole deformation increased, the
measured load decreased. After 30 tests (five months)
the measured average load at failure decreased by 11%.
Since the purpose of this test was to verify that the
production process was not changing, this apparent loss
in load carrying capacity could be erroneously interpreted
as a manufacturing problem instead of fixture wear. For
the other fixture and orientation, the lower maximum load
produced no significant fixture wear and stable month-to
month average load at failure readings, which verified that
the production process was not changing significantly
from month to month. Typical average maximum load
results are shown in Table II.
Table I. Average Material Properties of Ductile Iron Brake Anchors
Design Condition Microstructure UTS, MPa YS, MPa El, % E, GPaHardness,
BHN
A As-cast 20% F, 80% P 572 366 6.0 179 183
A Normalized >99% pearlite 824 517 3.6 170 270
A Normalized and 675oC tempered spheroidized pearlite 706 453 3.4 172 240
B As-cast 30% F, 70% P 603 373 9.9 177 190
B 730oC sub-critically annealed >99% ferrite 459 311 17.7 175 157
B Normalized >99% pearlite 855 522 4.3 172 258
B Normalized and 675oC tempered spheroidized pearlite 790 459 7.2 170 242
0
1,000
2,000
3,000
4,000
5,000
6,000
7,000
8,000
9,000
10,000
1.7 1.9 2.1 2.3 2.5 2.7
Relative Displacement, mm
Load,
N
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Figure 8a. Brake anchor design B driver side in the pull-test fixturebefore testing.
Figure 8b. Brake anchor design B driver side in the pull-test fixtureafter testing. Note: brake anchor fractures through the reducedsection or pocket.
Figure 9a. Brake anchor design B passenger side in the pull-testfixture before testing.
Figure 9b. Brake anchor design B passenger side in the pull-testfixture after testing. Note: brake anchor fractures through the fullsection and not through the reduced section.
pocket
pocket
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Table III. Effect of Loading Orientation on the Impact Properties of Brake Anchor Design B.
Average
Maximum
Load
(N)
Average Crack
Initiation
Energy (joules)
Average Deflection
at Crack Initiation
(mm)
Average Total
Absorbed Energy
(joules)
Average Total
Deflection
(mm)
Load Perpendicular to
Component12,827 46.15 5.08 77.23 10.74
Load Perpendicular to
Tie Bar9,196 39.53 6.97 62.73 14.00
Table IV. Impact Properties of Ductile Iron Brake Anchors Tested with the Load Applied Perpendicular to the Tie Bar.
Design Condition
Average
Maximum
Load (N)
Average Crack
Initiation Energy
(joules)
Average
Deflection at
Crack Initiation
(mm)
Average Total
Absorbed
Energy (joules)
Average
Total
Deflection
(mm)A As-cast 11,597 48.47 6.79 150.33 26.68A Normalized 14,697 69.24 7.68 173.10 26.18
A Normalized and tempered 12,878 121.87 12.73 215.85 27.40
B As-cast 9,196 39.53 6.97 62.73 14.00B Sub-critically annealed 7,744 85.59 14.30 132.03 26.13B Normalized 11,134 52.15 7.70 89.47 14.83B Normalized and tempered 10,542 95.42 12.84 146.68 24.48
Casting microstructure and chemistry, which determined
material properties, and casting design had a significant
effect on component performance. Ferrite is soft, weakand very ductile, pearlite is harder, stronger but less
ductile, and carbides are very hard, very strong and
brittle. Silicon decreases the amount of pearlite,
increases the strength of ferrite and suppresses carbides.
Therefore, the combination of material (microstructure and
chemistry) and casting design determined the ultimate
load bearing capacity and the ability to absorb impact.
When the two designs were compared using similar
loading conditions and similar microstructure, brake
anchor design A absorbed more energy initiating a crack
(22.6% for as-cast, 32.8% for normalized and 27.6% for
normalized and tempered) and more total energy (139.6%
for as-cast, 93.5% for normalized and 47.2% fornormalized and tempered) than brake anchor design B.
The impact properties as a function of heat treatment and
design are listed in Table IV.
The sub-critical annealing (softening) heat treatment
produced a slightly weaker but significantly tougher
component that was not as stiff as the as-cast
component, i.e., the load required to initiate a crack
decreased slightly, the energy absorbed during fracture
increased significantly, and the amount of deflection
during fracture increased significantly.
The normalizing (hardening) heat treatment produced a
significantly stronger and slightly tougher component tha
was approximately the same stiffness as the as-cas
component, i.e., the load required to initiate a crack
increased significantly, the energy absorbed during
fracture increased slightly, and the amount of deflection
during fracture was about the same.
The normalizing and tempering heat treatment produced a
slightly stronger and significantly tougher component tha
was not as stiff as the as-cast component, i.e., the load
required to initiate a crack increased slightly, the energyabsorbed during fracture increased significantly, and the
amount of deflection during fracture increased
significantly.
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CONCLUSIONS
1. In this study, a test that accurately simulated the
orientation and loading conditions on a vehicle was a
valuable proof test but was not the most appropriate
test for verifying that consistent product was being
produced month-to-month. For verifying product
consistency, a test that produced consistent resultswas critical. In this study, the loading conditions on
brake anchor design B - passenger side were such
that deformation of the test fixture could occur and
this deformation significantly affected the test data.
2. To properly compare similar components, the
orientation of the applied load must be consistent
(preferably in the worst case orientation).
3. In this study, brake anchor design A exhibited
consistently better impact properties due to a slightly
larger cross section and a more uniform cross
sectional shape that minimized stress risers and the
formation of carbides.
4. Heat treatment had a significant effect on the energyrequired to initiate a crack and the total energy
absorbed during fracture.
ACKNOWLEDGMENTS
The authors would like to acknowledge the assistance of
Dale tenPas (INTERMET Technical Center, Lynchburg,
VA), Ed Druschitz (summer intern) and Evan Shockley
(Governors School intern) for performing the pull and
impact tests, strain gage tests, metallography and tensile
tests. Melanie Folks is also acknowledged for performing
the various heat treatments on the castings evaluated in
this study.
CONTACT
Dr. Alan P. Druschitz received his PhD in Metallurgical
Engineering in 1982 from the Illinois Institute of
Technology, Chicago, IL. He is currently the Director of
Materials Research and Development for INTERMET
Corporation. He is located at the INTERMET Technical
Center, Lynchburg, VA 24502. He can be reached at
[email protected] or (434) 237-8749.
Before joining INTERMET Corporation, he was a staffresearch engineer for General Motors Corporation for
fourteen years. He has been a member of the American
Foundry Society for thirteen years, the Society of
Automotive Engineers for twenty years and ASM
International for twenty-five years. He is currently the Vice
President of the Ductile Iron Society, a member of the
Industrial Advisory Board for the Central Virginia
Governors School and a Member of the Governors Board
of Transportation Safety for the Commonwealth of Virginia.