effectiveness of the football helmet assessed by …
TRANSCRIPT
EFFECTIVENESS OF THE FOOTBALL HELMET ASSESSED BY
FINITE ELEMENT MODELING AND IMPACT TESTING
Liying Zhang, Dwarampudi Ramesh, King H. Yang, Albert I. King
Biomedical Engineering Department, Wayne State University
ABSTRACT
Mini-sled impact tests using a Hybrid III head-neck complex with and without a helmet were
conducted to contrast resulting head accelerations. Because this experimental configuration includes
both the linear and rotational impacts to the head, it represents the real world football impact
condition better than drop tests traditionally used to evaluate the protective effect of a helmet. It was
found that wearing a helmet significantly attenuates head linear acceleration but not angular
acceleration. Additionally, a 3-D finite element model of a football helmet simulating all of its
essential components was developed and validated to investigate its effectiveness in energy
attenuation. Results from these modeling and experimental efforts have shown that the helmet was
less effective in attenuating impact energy due to an impact to the front-boss and side of the helmet.
The validated helmet model can be used in conjunction with a validated human head model to design
helmets intelligently by determining optimal liner thickness and stiffness for omnidirectional
protection of the head, once an acceptable injury criterion is established. In addition, the helmeted
head model can be used as an inexpensive adjunct for current test procedures and for the
establishment of new procedures.
KEYWORDS: Helmet model, helmet impact testing, model validation, linear acceleration, angular
acceleration.
MILD TRAUMATIC BRAIN INJURY (MTBI) accounts for a majority of all traumatic head injuries
treated in emergency rooms, outpatient departments, and physicians’ offices in the United States. The
National Health Interview Survey (NHIS) estimated that more than 300,000 MTBIs or concussions
occur in sports or recreational activities each year. American football alone is responsible for more
than 100,000 annual brain injuries even though headgear was in use (Wilberger, 1993; Cantu, 1998).
While many of these injuries are mild, some can be quite serious, with long-term consequences.
Brain trauma exacts a huge societal cost in terms of healthcare, disability and years of productive life
lost. An estimated 2% of the US population lives with disabilities resulting from a traumatic brain
injury. Mitigation of brain injury is a major consideration in head protection. A better understanding
of the causal mechanisms of brain injury will allow us to develop better methods of prevention and
use them in the design of a safer environment.
Numerical models have been used in the automotive industry to design devices and restraint
systems to mitigate head/brain injury. However, the same technique has not been widely applied in
the helmet industry. Only a handful of lumped-parameter and finite element (FE) models of
motorcycle or bicycle helmets have been reported in the literature (Gilchrist and Mills, 1993; Yettran
et al., 1994; Brands et al., 1996) while there is virtually no FE football helmet model available. If
such a model can be developed and validated against experimental data, safety engineers can apply it
to develop better protection headgear.
On a separate but related issue, the Severity Index (SI) and maximum acceleration used in various
safety standards to regulate sports helmets are calculated from resultant linear acceleration. Although
IRCOBI Conference – Lisbon (Portugal), September 2003 27
many researchers still dispute the relative contribution of linear or angular accelerations that may
cause brain injury, research on the effects of angular acceleration was pursued more vigorously than
those of linear acceleration in recent times (Gennarelli et, 1987; Margulies and Thibault, 1992). As a
result, there is a current notion among some researchers that angular acceleration is largely
responsible for brain injury. It has been noted in the literature that the number of brain injury cases in
American football has been significantly reduced after regulatory organizations mandated the use of
the football helmet (Mertz et al., 1996; Cantu and Mueller, 2003). If indeed angular acceleration is
the primary source of brain injury, then a helmeted head should experience a lower angular
acceleration when compared to a bare head subjected to the same impact condition. Thus, the
objectives of this study were: 1) to develop a FE helmet model validated against a variety of impact
situations; and 2) to conduct a series of mini-sled head impact experiments to understand how the
resulting linear and angular head accelerations are reduced by wearing a helmet. In the future the
validated helmet model can be used in conjunction with an anatomically detailed human head model,
the Wayne State University head injury model (WSUHIM) developed by Zhang et al. (2001b), to
design helmets intelligently by determining optimal liner thickness and stiffness for omnidirectional
protection of the head, once an acceptable injury criterion is established. In addition, the helmeted
head model can be used as an inexpensive adjunct for current test procedures and for the
establishment of new procedures.
METHODS
Three sets of experimental data were either obtained from or conducted at external sources and one
series of mini-sled experiments was conducted in house to develop a FE model of a large size
Riddell® VSR-4 football helmet and to assess the changes in head acceleration on a dummy head by
adding a helmet to a Hybrid III head and neck complex. The VSR-4 helmet was selected because it is
the most commonly used helmet in the National Football League (NFL). Data acquired from other
sources included those provided by Biokinetics and Associates, Ltd. (Ottawa, Canada) based on
ASTM helmet impact test protocol and those conducted at Denton ATD (Detroit, Michigan) based on
standard Hybrid III dummy head drop tests and neck calibration tests. The experiments conducted in
this study were mini-sled tests using a Hybrid III head and neck complex, with or without a VSR-4 or
a BIKE® helmet. Data obtained from the Hybrid III head calibration test and neck calibration test
were used to develop and validate a FE model of the Hybrid III head and neck complex. Additional
material properties needed for the Hybrid III head and neck model development were obtained from
compression tests using an Instron testing machine. For the VSR-4 helmet model, properties of the
comfort liner were derived from results of ASTM tests, using a reverse engineering approach. The
helmet model was then integrated with the Hybrid III head and neck model. Predictions made by the
combined model were compared with experimental results obtained from mini-sled tests. The
following sections describe different experimental and model development procedures employed in
this study.
EXPERIMENTAL METHODS:
ASTM Helmet Impact Tests: ASTM F717-89/95 is a standard test method to determine energy
attenuation characteristics of protective headgear for football recommended by the American Society
for Testing and Materials (ASTM) Committee on Standards (ASTM, 1989). Prior to the test, a
football helmet is mounted over a rigid ISO/DIS headform that can be oriented in any of the six
different positions and dropped at a specified velocity of 5.47 m/s onto a fixed metal anvil, covered by
a material with a durometer value of 38 shore “A”. Three impacts on each of the six locations,
namely crown, front, front boss, side, rear boss, and rear, are required. A triaxial accelerometer,
mounted at the center of gravity (C.G.) of the headform, is used to record the acceleration histories for
each impact location. The average maximum acceleration at each location shall not exceed 275 g.
These test results were used to tune the properties of the helmet comfort liner for the development of
the helmet model.
Hybrid III Head Drop Tests: According to the Code of Federal Regulations (Part 572), the
acceleration measured at the C.G. of a Hybrid III dummy head assembly needs to fit into a prescribed
corridor when it is dropped from a height of 376 mm onto a flat steel plate. The acceleration time
IRCOBI Conference – Lisbon (Portugal), September 2003 28
histories obtained from this type of tests were used to validate the Hybrid III head model to be
described later.
Hybrid III Neck Calibration Tests: Standard Hybrid III neck calibration impact tests were
conducted at a velocity of 7.06 m/s for the flexion test and 6.07 m/s for the extension test. During the
calibration procedure, head and neck rotations were measured and the histories of D-plane rotation
were calculated from those measurements. Here the D-plane rotation is defined as the rotation of the
base of the head relative to the pendulum. The main purpose of this set of test was to provide needed
data to validate the Hybrid III neck model, for both flexion and extension.
Mini-Sled Impact Tests: A series of mini-sled experiments was conducted to determine changes in
head accelerations when a football helmet was added to a Hybrid III head and neck complex. Bare
head impact tests were conducted first. Data obtained from these tests were used as a baseline for
comparison with helmeted head linear and angular acceleration data and to validate the Hybrid III
head-neck model. Two helmets, a Riddell® VSR-4 and a BIKE, were securely attached to the
Hybrid III head later and experiments repeated. These two helmets were selected because they were
commonly used by NFL players. Additionally, data obtained from the VSR-4 helmet test were used
to provide unique information to validate the integrated Hybrid III head and VSR-4 helmet model.
The impact tests were conducted by mounting
the head and neck complex of a Hybrid III dummy
onto a custom-designed fixture that was attached
to a pneumatically driven mini-sled (Figure 1).
This fixture was also designed to allow the head-
neck complex to be oriented in three major impact
directions (frontal, lateral, and front-boss or 45
degree oblique) to simulate typical head collisions
observed in football accidents. Impact velocities
of 5 and 7 m/s were selected for the bare head
impacts and velocities of 7 and 10 m/s were used
for the helmeted head impacts. The impact
surface was a 300-mm square foam block with a
thickness of 76 mm. It was attached firmly to a rigid barrier. The foam surface was sloped rearward
at a 30-degree angle to the vertical or Z-axis of the head coordinate system to avoid engagement of the
facial features of the Hybrid III head assembly during impact. For the impact surface, four different
types of foam material with varying densities were tested in order to simulate different impact
conditions. The selected foams were made of Expanded Polyproplyrene (EPP), Expanded
Polystyrene (EPS), GECET, and Polyurethane (Foamex). The Hybrid III head was instrumented with
a 3-2-2-2 nine-accelerometer array to measure all six components of head linear and angular
accelerations. Each impact configuration was repeated once and the averaged data were reported.
Fig. 1 - Schematic diagram of the mini-sled
test configuration.
MODEL DEVELOPMENT METHODS:
All simulations were performed using a nonlinear explicit finite element solver LS-DYNA version
960 (LSTC, Livermore, California). The following section describes relevant steps taken in the model
development process.
Football Helmet Model: Only the VSR-4 helmet model was developed in this study. The helmet
model consisted of an outer shell, energy absorbing liners, comfort liners, jaw pads, a facemask, and a
chinstrap. The geometry of the helmet was obtained by digitizing the physical helmet using a
MicroScribe® 3-D digitizer (Immersion Corporation, San Jose, California). Because the digitizer was
too small to reach some of the inner surfaces of the padding systems within the shell, components of
the padding and liner systems within the shell were detached from the shell and digitized separately.
The digitized profiles of the helmet shell, helmet liners and facemask were used to generate surface
data, using the Pro/ENGINEER® software (Parametric Technology Corporation, Needham, MA).
Based on these surface data, a finite element mesh of the helmet was developed using the
HyperMesh pre-processor, (Version 3.1, Altair Engineering, Inc., Troy, Michigan). The headform
used in the standard ASTM test was also modeled. The same 3-D digitizing method was used to
obtain the surface of the headform and the surface data were then meshed into a rigid body headform
model.
IRCOBI Conference – Lisbon (Portugal), September 2003 29
The entire helmet model was composed of about 20,400 nodes, and 25,600 elements, not including
the headform. The outer shell of the helmet was found to have a uniform thickness of 3.9 mm. The
protective liners for frontal, side, crown, and rear regions were meshed separately to incorporate
various thickness and material definitions. The thickness of the energy absorbing liners at the crown,
front, rear and side was measured and found to be 26, 25, 13, and 13 mm, respectively. A total of
8,716 brick elements arranged in three or more layers across the thickness were generated for all
energy absorbing liners. In the actual helmet, the outer surface of the liners was firmly attached to the
inner surface of the shell. Thus, no relative motion was allowed at this interface. Snap in jaw pads
were modeled with 854 solid elements and directly connected to the nodes of the outer shell. A
thickness of 20 mm was defined for the jaw pad based on a direct measurement of the prototype. The
comfort liners at the crown, rear and side regions were modeled as solid elements with a thickness
that ranged from 6 to 10 mm. These elements were covered with a layer of shell elements of varying
thickness (0.8 to 1.8 mm). The comfort liners were meshed by a total of 4,994 elements. The steel
facemask, or faceguard was meshed with 2,590 of shell elements which were assumed rigid. The total
mass of the FE VSR-4 model was 1.24 kg (excluding the face mask), matching that of the actual
helmet. Figure 2 shows the three-dimensional FE model of a Riddell® VSR-4 football helmet.
Energy Liner
-Crown Pad
-Frontal Pad
-Jaw Pad
Comfort Liner
-Crown Pad
-Side Pad
-Rear Pad
Impact Liner
-Rear, Side Pads
(a) (b)
Fig. 2 - Helmet model overview and a half model showing the interior energy absorbing liner and
comfort liner structure.
The helmet outer shell, made of molded Kara-lit® polycarbonate produced by GE, was assumed to
have a Young’s modulus of 1.7 GPa. The material definition for the liners was either based on data
obtained from manufacturers, acquired experimentally, or using a reverse engineering method.
Energy absorbing liners of the Riddell® VSR-4 helmet were made of vinyl nitrile and polyurethane
foam which are stiff but highly compressible elastic foam materials. An elastic foam material model
was defined for the energy absorbing liner material and the properties were based on the data provided
by its manufacturer. As for the jaw pad liner, the material properties were obtained from a
compression test. Comfort liners used at the crown, rear and brow are polyurethane and polyester
foams. The material characteristic of these types of foam was modeled as an inelastic crushable foam.
Simulations of the standard ASTM football helmet tests were carried out to obtain the material
properties of the comfort liner using reverse engineering methods. To simulate the impact test, the
integrated helmet and headform model was given an initial velocity of 5.47 m/s prior to impacting a
flat rubber surface, mounted on a rigid body representing fixed metal anvil. A penalty based contact
interface definition with a coefficient of friction of 0.3 was assigned between the headform and the
inner surface of the helmet. The helmet model was positioned in six orientations to conform to the
impact locations specified by the ASTM standard. By continuously tuning the elasticity of the
comfort liner material parameters, the predicted headform acceleration response matched
experimental measurements from ASTM tests. Table 1 lists the properties of major components used
in the helmet model.
Hybrid III Dummy Head and Neck Model: A Hybrid III head and neck model was needed because
the mini-sled impact tests used a Hybrid III dummy head and neck complex. Therefore, a Hybrid III
head and neck model was also developed. An accurate solid model of the head assembly was meshed
from CT scan data of the head of a Hybrid III 50th percentile male dummy. The head model was
constructed with 4,350 solid elements with a mass of 4.54 kg (Figure 3a). The moment of the inertia
IRCOBI Conference – Lisbon (Portugal), September 2003 30
was in accordance with published data (Kaleps and Whitestone, 1988). The deformable skin was
modeled as viscoelastic solid elements. The material properties of the vinyl skin were derived from
basic vinyl material tested in compression at rates of 0.1, 0.5, and 1.0 m/s. It was found that the vinyl
skin was not remarkably rate sensitive in the range tested. Consequently, average values were used to
define the property of vinyl skin.
Table 1 - Material properties assumed for the helmet model.
Substructure Material Model ρ (kg/mm3) E (MPa) ν
Shell Elastic 1.36E-06 1.7E+03 0.40
Energy Brow Elastic Foam 2.8E-07 8E-01 0.01
Liner Crown 1.2E-07 8E-02 0.01
Side 2.02E-07 5E-01 0.01
Rear 2.02E-07 5E-01 0.01
Comfort Crown Inelastic 3.0E-08 4.48E-02
Liner Side Crushable foam 7.0E-08 3.4E-01
Rear 7.0E-08 3.4E-01
Jaw Liner Elasto-plastic 1.2E-07 1.0E-01 0.01
Chin Strap Elasto-plastic 4.19E-06 2.4E+03 0.4
The geometry of the neck assembly was taken from the manufacture’s drawings. It is composed of
four butyl rubber segments sandwiched between five aluminum discs. The aluminum plates were
modeled as rigid solid elements. Each rubber segment has a partial depth horizontal slit on the
anterior side with a different depth at each level to yield the prescribed neck shape during bending.
These slits were explicitly modeled and surface-to-surface contact was defined for each slit. Elements
adjacent to the slit were covered with shell elements and were integrated using a full integration
scheme to avoid hourglassing due to excessive deformation. The rest of rubber intervertebral discs
was modeled as a viscoelastic solid, and a reduced integration scheme with hourglass treatment was
used.
The occipital condyle was represented by a revolute joint. The entire neck assembly was
constructed with 4,190 elements (Figure 3b) having a mass of 1.54 kg. Figure 3c shows the integrated
head-neck model. Butyl rubber material properties were obtained by compressing a neck rubber
segment at rates of 0.05, 0.1, 0.5, and 1.0 m/s to a maximum compression of 20% and a load of 8,500
N. The decay constant for the neck rubber was estimated to be 0.05 s-1. The properties used for the
neck model are listed in Table 2. The rotational stiffness of the occipital condyle joint was calculated
by dividing the moment by the angle of the occipital condyle measured during neck pendulum tests.
It was found that the joint stiffness determined using this method was lower than those used by
Seemann et al. (1986), Wismans and Hermans (1988), Deng (1989) and Yang and Le (1992).
(a) Head model (b) Neck model (c) Head and neck assembly
Fig. 3 - Hybrid III head and neck model.
Table 2 – Material properties assigned for the neck model. Structure Material Model Density (kg/mm3) E (MPa) υ
Neck Rubber Viscoelastic 1.05E-06 1.18E+01 0.48
Aluminum* Rigid 2.70E-06 6.89E+04 0.38
*: Although the aluminum plate was defined as rigid body, the Young’s modulus was still needed for contact
detection.
IRCOBI Conference – Lisbon (Portugal), September 2003 31
MODEL VALIDATION PROCEDURES:
Head-Neck Model Validation: The head model was validated against data obtained from head drop
tests while the head-neck model was validated against neck pendulum test procedures required by the
Code of Federal Regulations (Part 572). To simplify the head-neck model simulation, the measured
pendulum acceleration profile from the test was used as input to the model without the modeling of
the Hexcel block (honeycomb) used in the test. Neck D-plane rotation time histories predicted by
model from the simulation of the flexion and extension tests were compared to the acquired
experimental data. Additionally, the head-neck model was validated against data obtained from bare
head to foam block impact using a mini-sled. The foam material properties used in the model were
derived by dropping a weight onto various foams. Only the frontal impact simulations were
performed because impacts in the other directions were not conducted for unhelmeted head-neck
complex on the mini-sled (Figure 4a). Two different foam materials (EPP 4.2 and 3.0) were
simulated for the bare head impact. The sled with its payload was given an initial impact velocity of 7
m/s. Impact force and linear and rotational accelerations predicted by the model were compared with
experimental measurements.
Helmet Model Validation: The helmet model, developed using results from the ASTM tests, was
validated against data obtained from testing of a helmeted head-neck complex mounted on the mini-
sled (Figures 4b, c and d). The moving sled plate was represented by a small block with a mass equal
to that of actual sled plate. The nodes on the back surface of the foam block where the rigid barrier
was located were defined as rigid. To simulate helmeted head impacts, the Riddell helmet model,
identical to that used in the mini-sled tests, was integrated with the validated Hybrid III head-neck
model. A sliding interface with a coefficient of friction of 0.7 was used to represent the interaction
between the head and the helmet. Three impact directions, namely the frontal, lateral and front-boss,
were simulated. The same procedures used for the bare head impact tests were also used for this
series of helmeted head impact validations.
Foam
Block
Sled Plate
(a) (b) (c) (d)
Fig. 4 - Simulation of the test set up of a Hybrid III head-neck complex impacting a foam material: (a)
Unhelmeted frontal impact; (b) Helmeted frontal impact; (c) Helmeted front-boss impact; (d)
Helmeted lateral impact.
RESULTS
MODEL PERFORMANCE SIMULATING THE ASTM IMPACT TESTS:
Figure 5 shows a comparison of the resultant acceleration-time traces of the headform between
three experimental measurements and model predictions at crown, frontal, side, and rear locations.
The predicted peak resultant accelerations at the C.G. of the headform for crown, frontal, side and rear
impacts were 112, 162, 198, and 189 g, respectively. They were within 4% of the average
experimental head acceleration response for the corresponding impact conditions. In addition, the
corresponding impact durations from model simulation were quite comparable with those observed
experimentally. Overall, the comparison results indicated that the model was capable of capturing
head resultant translational acceleration-time traces, in the absence of any head rotation, for the
specified impact directions.
SIMULATION OF THE HYBRID III HEAD AND NECK CALIBRATION TESTS:
IRCOBI Conference – Lisbon (Portugal), September 2003 32
Figure 6a shows the resultant head acceleration predicted by the model compared to experimental
measurement during a Hybrid III head drop test. The HIC value calculated by the model was 776 in
comparison with 758 obtained from experimental data. Model results were within 5% of the
experimental values. The D-plane rotation histories predicted by the model are compared with
experimental data, as shown in Figures 6b and 6c. The model predictions agreed well with
experimental data and were well within the range of peak rotations specified for this test (error bar).
Also, the opening of the slits simulated during extension and the compressive contact of the slits
during flexion resembled the phenomena seen experimentally (Figure 7).
Accele
ration (
g)
A
ccele
ration (
g)
Fig. 5 - Comparison of head acceleration between model results and experimental data from ASTM
football helmet drop tests: crown, frontal, side and rear impact.
Head Drop Resultant Acceleration
0
40
80
120
160
200
240
280
320
0 1 2 3 4 5 6Time (ms)
Acce
lera
tio
n (
g)
Model
Test
Neck Pendulum Flexion
-60
-40
-20
0
20
40
60
80
0 0.05 0.1 0.15 0.2
Time (s)
D-P
lan
e R
ota
tio
n
(Deg
rees)
Experiment
Model
Neck Pendulum Extension
-40
-20
0
20
40
60
80
100
120
0 0.05 0.1 0.15 0.2
Time (s)
D-P
lan
e R
ota
tio
n
(Deg
rees)
Experiment
Model
(a) (b) (c)
Fig. 6 – Validation of the head and neck model against the standard Hybrid III dummy head drop test
and head-neck pendulum test: (a) Head resultant acceleration; (b) D-plane rotation in flexion; (c) D-
plane rotation in extension.
Fig. 7 – Neck flexion and extension test simulation.
IRCOBI Conference – Lisbon (Portugal), September 2003 33
SIMULATION OF THE MINI-SLED IMPACT TESTS:
Figure 8 shows model validation results for a bare head impact against EPP 3.0 pcf (pounds/cubic
foot) foam at 7 m/s impact velocity. The difference between the model and test data is summarized in
Table 3. Overall, the contact force magnitude predicted by the model matched well with experimental
data. The maximum difference in translational acceleration of the head between model prediction and
experimental data was 10.5%. The duration of the contact force and acceleration was slightly shorter
as predicted by the model. The maximum difference in peak rotational acceleration was 8.4%.
For helmeted head-neck mini-sled impact simulations, the model responses followed the
experimental data with varying degrees of correlation, both in magnitude and in trend. Figure 9
shows a comparison of impact force and head acceleration histories between model results and those
obtained experimentally for frontal impact against EPP 4.2 pcf foam at an impact velocity of 7 m/s.
The predicted impact force and translational acceleration were about 9.8% and 5.7% higher than those
measured experimentally. However, the rotational acceleration predicted by the model tended to be
lower than that of the test data with a difference of 7.4%. For both the front boss and side impact
simulations, resultant translational and rotational accelerations predicted by the model were within 7%
of the experimental results (Figures 10 and 11). The maximum difference in peak force between
model predictions and test data was no more than 10%. However, the model was not capable of
capturing the second peak in the force time histories seen experimentally (Figures 9, 10 and 11).
Frontal Impact Without Helmet
-6000
-4000
-2000
0
0 5 10 15 20
Time (ms)
Fo
rce
(N
)
Model
Test
Frontal Impact Without Helmet
-1600
-1200
-800
-400
0
400
0 10 20 30 4
Time (ms)
Acc
ele
rati
on
(m
/s2)
0
Model
Test
Frontal Impact without Helmet
-10000
-6000
-2000
2000
6000
0 5 10 15 20
Time (ms)
Accele
rati
on
(ra
d/s
2) Model
Test
Fig. 8 - Comparison of force and linear and rotational head acceleration between model results and
experimental data for a bare head impact at 7 m/s against EEP foam with a density of 3.0 pcf.
Table 3 – Comparison of the model predictions and experimental data for impact with and without
helmet in mini-sled test. Impact Condition Peak Response Experiment Simulation % diff.
Without Force (N) -5596 -5400 -3.5
helmet Frontal Linear Accel. (m/s2) -1130 -1250 +10.5
Rotational Accel. (rad/s2) -8666 -7940 -8.4
Force (N) -4745 -5210 +9.8
Frontal Linear Accel. . (m/s2) 911 963 +5.7
Rotational Accel. (rad/s2) 8010 7420 -7.4
With Force (N) -5037 -5450 +8.2
helmet Front-Boss Linear Accel. . (m/s2) 982 988 +0.6
Rotational Accel. (rad/s2) 8274 8390 +1.5
Force (N) -5059 -5538 +9.5
Side Linear Accel. . (m/s2) -1190 -1124 -5.6
Rotational Accel. (rad/s2) 10532 11300 +7.2
IRCOBI Conference – Lisbon (Portugal), September 2003 34
Frontal Impact with Helmet
-6000
-4000
-2000
0
0 5 10 15
Time (ms)
Fo
rce
(N
)
Model
Test
Frontal Impact with Helmet
-200
200
600
1000
0 5 10 15 20
Time (ms)
Ac
ce
lera
tio
n (
m/s
2)
Model
Test1
Frontal Impact with Helmet
-4000
-2000
0
2000
4000
6000
8000
0 5 10 15
Time (ms)
Acc
ele
rati
on
(ra
d/s
2)
Model
Test
Fig. 9 - Comparison of force, linear and rotational head acceleration between model responses and
experimental data for a helmeted frontal impact at 7 m/s velocity against EPP (4.2 pcf) foam.
Frontal Boss Impact with Helmet
-7000
-5000
-3000
-1000
1000
0 5 10 15 20
Time (ms)
Fo
rce
(N
)
Model
Test
Frontal Boss Impact with Helmet
0
200
400
600
800
1000
1200
0 2 4 6 8 10 12 14 16 18 20Time (ms)
Ac
ce
lera
tio
n (
m/s
2)
Test
Model
Frontal Boss Impact with Helmet
0
2000
4000
6000
8000
10000
0 5 10 15 20
Time (ms)
Ac
ce
lera
tio
n(r
ad
/s/s
)
Model
Test
Fig. 10 - Comparison of force, linear and rotational head acceleration between model responses and
experimental data for a helmeted front-boss impact at 7 m/s velocity against EPP (4.2 pcf) foam.
Side Impact with Helmet
-7000
-5000
-3000
-1000
1000
0 5 10 15
Time (ms)
Fo
rce
(N
)
20
Model
Test
Side Impact with Helmet
-1200
-800
-400
0
400
0 5 10 15 20 25
Time (ms)
Acc
ele
rati
on
(m
/s2)
Model
Test
Side Impact with Helmet
0
2000
4000
6000
8000
10000
12000
0 5 10 15 20 25 30
Time (ms)
Acce
lera
tion
(ra
d/s
2)
Model
Test
Fig. 11 - Comparison of force, linear and rotational head acceleration between model responses and
experimental data for a helmeted side impact at 7 m/s velocity against EPP (4.2 pcf) foam.
MINI-SLED EXPERIMENTAL RESULTS:
Table 4 summarizes the translational and rotational accelerations and HIC obtained from helmeted
mini-sled experiments at a speed of 7 m/s. Each impact test was repeated once and the averaged data
were reported. Impacts from the side and front-boss directions produced higher translational head
accelerations compared to those seen in frontal impact at the same impact velocity. Impacts to the
frontal and the frontal boss regions produced nearly the same amount of rotational acceleration
whereas impact to the side of the helmet resulted in the lowest rotational acceleration. The HIC value
was the highest for front-boss impacts followed by side impacts.
Table 4 - Head resultant acceleration and HIC values for different impact locations Riddell Helmet
7 m/s
Frontal
Impact
Front-Boss
Impact
Side
Impact
Mean T. Accel. (g) 89 97 103
Mean R. Accel. (rad/s2) 7790 7772 6504
HIC15 382 436 398
Figure 12 shows a comparison of linear and rotational head accelerations with and without either
the BIKE® or Riddell® helmet for frontal impacts at 7 m/s into a variety of foams. Results clearly
showed that the translational head acceleration decreased by as much as 29.5% for the Riddell®
helmet and 22.1% for the BIKE® helmet, in comparison with unhelmeted impact data. On the other
IRCOBI Conference – Lisbon (Portugal), September 2003 35
hand, changes in the peak rotational acceleration due to the use of both helmets were small and
inconsistent with the average reduction of only 5.6%.
Frontal Impact , 7 m/s
0
20
40
60
80
100
120
140
160
180E
PP
1.5
EP
P 2
.0
EP
P 3
.0
EP
P 4
.2
EP
S 1
.5
EP
S 3
.0
EP
S 4
.0
GE
CE
T 4
.0
FO
AM
EX
4.0
Tra
nsla
tio
nal A
ccele
rati
on
(g
)
Without Helmet
With BIKE Helmet
With Riddell Helmet
Frontal Impact , 7 m/s
0
2,000
4,000
6,000
8,000
10,000
12,000
14,000
EP
P 1
.5
EP
P 2
.0
EP
P 3
.0
EP
P 4
.2
EP
S 1
.5
EP
S 3
.0
EP
S 4
.0
GE
CE
T
4.0
FO
AM
EX
4.0
Ro
tati
on
al
Ac
ele
rati
on
(ra
d/s
2) Without Helmet
With BIKE Helmet
With Riddell Helmet
Fig. 12 - Comparison of acceleration measured at the head C.G. without a helmet and with a BIKE
and Riddell helmet for impacts conducted at 7 m/s.
DISCUSSION
A 3D FE model of a VSR-4 football helmet has been developed and validated against mini-sled
impact tests during which both linear and rotational acceleration were involved. In addition, a Hybrid
III head model and a Hybrid III head-neck model was developed and validated against data obtained
from the standard head drop test and head-neck pendulum test, respectively. Overall, the computer
models developed were capable of duplicating the dynamic response of the system seen
experimentally. However, the correlation of model to the experimental data varied with different
impact conditions.
For bare head frontal mini-sled impact simulations, slightly larger discrepancies in rotational
acceleration, especially during the acceleration period, were observed between the model and
experimental results. This was probably related to our inability to identify the precise point of contact
between the forehead and the foam surface during the actual test. A small variation in the point of
contact with respect to the C.G. of the head could significantly affect the magnitude of the computed
rotational acceleration. Another source of discrepancy is the existence of the small clearance between
the sled plate and the sled rail that could induce unexpected vertical motions during impact as
observed in the high-speed video. Improved stability of the mini-sled should reduce the variations.
As for the validation of helmeted head impacts, rotational acceleration in frontal impact was
generally under-predicted even though the predicted contact force and linear acceleration from model
were higher than those seen experimentally. One reason for the discrepancy could be due to the
sliding definition and the assigned friction coefficient between the head and helmet in the model. Part
of the rotational energy could be dissipated due to relative sliding occurring between the head and
helmet in the model and it might not be the case in the actual test. Notice that experimentally
obtained force response generally exhibited a second peak, while the model was not capable of
predicting this trend. High-speed video footage taken during the mini-sled tests was reviewed to
decide the potential source of discrepancy. It was found that there was a slight upward motion of the
sled due to a minute clearance between the sled and rail, especially for impacts involving stiffer
materials (e.g. EPP 4.2). This could induce a second contact between the helmet and foam block
experimentally which could not be simulated by the model. In addition to a better characterization of
foam material properties, fine-tuning of the helmet model may be needed to further improve model
predictions.
In terms of the liner material used in the current VSR-4 helmet, the model indicated that
compression of the liner was 90% or higher during side and rear impacts. This may imply that a
different foam is needed to maximize the energy attenuation capacity in these areas. In addition, more
deformation or shell bending was predicted by the model in a side and rear impact compared to other
impact sites. These observations indicate that there is room for improving the current helmet design
in terms of structural and material optimizations.
IRCOBI Conference – Lisbon (Portugal), September 2003 36
IRCOBI Conference – Lisbon (Portugal), September 2003 37
Three ASTM tests were conducted for each of the six impact locations while linear accelerations
were measured at the C.G. of the ISO/DIS headform. The resultant linear head acceleration ranged
from 116 to 210 g’s with the highest response occurring during a lateral impact. According to the
performance criterion currently specified in the ASTM standard, the helmet passed the tests.
However, these data clearly indicate that the current helmet design does not offer equal protection to
the head for impacts coming from different directions. Analysis of data obtained from the mini-sled
impact tests, a different experimental approach conducted in this study, also demonstrated that the
head experienced the highest response in front-boss (oblique 45 degree) impacts in comparison with
other directions in terms of peak linear acceleration or HIC values. Therefore, if brain injury could be
mitigated by reducing translational head acceleration, both the drop test and mini-sled test results
suggest that the head received less protection from the current helmet if impacts were delivered to the
front-boss region and to the side of the helmet.
In all existing helmet standards, the assessment of helmet energy attenuation performance utilizes a
single criterion regardless of impact location. An analysis of MTBI data obtained from the NFL
database revealed that 40% (10 out of 25) concussion cases were due to an impact located in the 45-
90 degree quadrant of the helmet, 36% were the result of impacts in the 0-45 degree quadrant and
18% in the 90-150 degree quadrant (Zhang et al., 2003). In a previous study using a FE human head
model, it was shown that the human head had a decreased tolerance to lateral impact in comparison
with an impact from the frontal direction (Zhang et al., 2001b). Animal models of concussion and
diffuse axonal injury studies (Hodgson et al., 1983; Gennarelli et al., 1987) also showed that animals
sustained a more severe form of brain injury from lateral impacts than from other impact directions.
Low tolerance of the head to lateral impact in comparison with frontal impact was also observed in
cadaver tests conducted by Tarriere (1985). Data obtained from field accident, animal and cadaver
experimental studies, mathematical modeling, along with that obtained from this study all suggest that
directional sensitivity of the head/brain need to be taken into account in helmet design.
No clear trend can be established when comparing rotational accelerations for bare and helmeted
heads during mini-sled testing of the Hybrid III head and neck complex. For the BIKE® helmet, four
of the nine foams tested resulted in reduced angular accelerations while seven of the nine foams tested
resulted in reduced angular accelerations when a Riddell® helmet was used. On the other hand, linear
accelerations were significantly reduced for both helmets, under all test conditions. The average
reduction in rotational acceleration was only 5.6% compared to an average reduction of 26% in linear
acceleration when a helmet is worn. Thus, it can be concluded that both helmets tested are effective
in reducing the head translational acceleration due to the padding but had little or no effect on
rotational acceleration. This phenomenon makes physical sense. Padding in a helmet increases the
contact area with the head and thus reduces the peak force and linear acceleration. However, the
magnitude of an impact-induced angular acceleration is a function of the location of impact with
respect to the C.G. of the head-neck system, the rotational moment of inertia, and magnitude of the
contact force. Because these parameters are very similar for both the bare and helmeted head test
configurations, it is understandable that the two helmets studied are not effective in reducing
rotational acceleration.
CONCLUSIONS
1. A three-dimensional FE model of a football helmet has been developed. To the best of our
knowledge, this is the first FE model that simulates all the essential components of a football
helmet. Additionally, a Hybrid III head-neck complex was also developed and validated.
2. The helmet-head-neck model was validated against experimental data obtained from mini-sled
tests subjected to both linear and angular motions.
3. The structural and material characteristics of the helmet tested were not optimized to protect
head against impacts from front-boss and side of helmet.
4. Under a limited number of impact conditions, the two football helmets tested significantly
attenuated the head translational acceleration but were less effective in reducing rotational
acceleration.
5. Current helmet designs need to be improved to offer 360-degree protection.
IRCOBI Conference – Lisbon (Portugal), September 2003 38
ACKNOWLEDGMENTS
This research was supported in part by a grant from National Football League Charities for the
study of Mild Traumatic Brain Injury. The opinions expressed here are those of the authors and do
not necessarily reflect those of the National Football League.
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