U.S. patent application number 15/338858 was filed with the patent office on 2018-05-03 for vehicle structure.
This patent application is currently assigned to Nissan North America, Inc.. The applicant listed for this patent is Nissan North America, Inc.. Invention is credited to Hideo AIMOTO, Joseph Bruno BURATTO, Matthew Michael GAPINSKI, Patrick Dean GRATTAN, Christopher Robert HARTLEY, Kazunori IIMI, Naoki KAMIZAWA, Gunnar MASON, Perry MCCONNELL, Michael James MCGORY, Takemi NISHIKAWA, Takao TANI, David James WOZNIAK.
Application Number | 20180118267 15/338858 |
Document ID | / |
Family ID | 62016740 |
Filed Date | 2018-05-03 |
United States Patent
Application |
20180118267 |
Kind Code |
A1 |
IIMI; Kazunori ; et
al. |
May 3, 2018 |
VEHICLE STRUCTURE
Abstract
An off-center impact reinforcement structure includes a push arm
and a first diagonals structure installed to elements of a frame of
a vehicle structure. The push arm is coupled to the frame proximate
an intersection of a first side member and a first cross-member and
extends in a forward and laterally outboard direction from the
intersection. The first diagonal structure extends rearward and
laterally inboard from proximate the intersection toward a section
of a second side member rearward of the first cross-member. The
off-center impact reinforcement structure is configured such that
during an off-center impact event in which a stationary barrier
impacts against a front surface of the push arm during forward
movement of the vehicle frame, impacting forces from the impact
event are transferred through the push arm to the vehicle frame at
the intersection and from the intersection to the first diagonal
structure.
Inventors: |
IIMI; Kazunori; (Atsugi,
JP) ; NISHIKAWA; Takemi; (Atsugi, JP) ; TANI;
Takao; (Tokyo, JP) ; AIMOTO; Hideo; (Atsugi,
JP) ; KAMIZAWA; Naoki; (Toda, JP) ; HARTLEY;
Christopher Robert; (West Bloomfield, MI) ; GRATTAN;
Patrick Dean; (Wixom, MI) ; BURATTO; Joseph
Bruno; (Beverly Hills, MI) ; MCCONNELL; Perry;
(Farmington Hills, MI) ; WOZNIAK; David James;
(Canton, MI) ; MCGORY; Michael James; (West
Bloomfield, MI) ; MASON; Gunnar; (Holly, MI) ;
GAPINSKI; Matthew Michael; (West Bloomfield, MI) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Nissan North America, Inc. |
Franklin |
TN |
US |
|
|
Assignee: |
Nissan North America, Inc.
|
Family ID: |
62016740 |
Appl. No.: |
15/338858 |
Filed: |
October 31, 2016 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B62D 21/05 20130101;
B62D 25/08 20130101; B62D 21/155 20130101; B62D 21/02 20130101;
B62D 21/06 20130101; B62D 21/11 20130101 |
International
Class: |
B62D 21/15 20060101
B62D021/15; B62D 21/05 20060101 B62D021/05; B62D 21/03 20060101
B62D021/03; B62D 21/06 20060101 B62D021/06; B62D 25/08 20060101
B62D025/08; B62D 21/11 20060101 B62D021/11 |
Claims
1. A vehicle structure comprising: a vehicle frame having a first
side member, a second side member, a first cross-member and a
second cross-member, the first side member and a second side member
extending from a front portion of the vehicle frame to a rear
portion of the vehicle frame, the first cross-member extending in a
vehicle lateral direction and being rigidly fixed to front areas of
each of the first side member and the second side member, the
second cross-member extending in the vehicle lateral direction and
being rigidly fixed to areas of each of the first side member and
the second side member rearward from the first cross-member
defining an engine receiving space between the first and second
cross-members and the first and second side members; and an
off-center impact reinforcement structure including: a push arm
coupled to the vehicle frame proximate an intersection of the first
side member and the first cross-member and extending in a forward
and laterally outboard direction from the intersection of the first
side member and the first cross-member; a first diagonal structure
extending rearward and laterally inboard from proximate the
intersection of the first side member and the first cross-member
toward a section of the second side member rearward of the first
cross-member; the off-center impact reinforcement structure being
configured such that during an initial stage of an off-center
impact event in which a stationary barrier impacts against a front
surface of the push arm during forward movement of the vehicle
frame, impacting forces from the off-center impact event are
transferred through the push arm to the vehicle frame at the
intersection of the first side member and the first cross-member,
and further from the intersection of the first side member and the
first cross-member to the first diagonal structure.
2. The vehicle structure according to claim 1, further comprising a
second diagonal structure extending from a mid-portion of the
second cross-member rearward to a section of the second side member
rearward of the second cross-member, and the first diagonal
structure extends rearward to the mid-portion of the second
cross-member forward of the second diagonal structure.
3. The vehicle structure according to claim 2, wherein the
off-center impact reinforcement structure is further configured
such that during the initial stage of the off-center impact event
against the front surface of the push arm, impacting forces from
the off-center impact event are further transferred from the
mid-portion of the diagonal structure to an area of the second side
member rearward of the second cross-member.
4. The vehicle structure according to claim 1, wherein the
off-center impact reinforcement structure is further configured
such that during a second stage of the off-center impact event
immediately after the initial stage of the off-center impact event,
a rear surface of the push arm contacts the vehicle frame at the
intersection of the first side member and the first cross-member
and pivots about the intersection of the first side member and the
first cross-member such that the a front surface of the push arm
moves in a laterally outboard direction away from the first side
member and a rearward direction.
5. The vehicle structure according to claim 4, wherein the
off-center impact reinforcement structure is further configured
such that after the second stage of the off-center impact event the
push arm is moved to a position parallel to or in alignment with
the first cross-member.
6. The vehicle structure according to claim 4, wherein during the
second stage of the off-center impact event impacting forces acting
on the push arm urge the vehicle frame to move in a lateral
direction away from the stationary barrier.
7. The vehicle structure according to claim 1, further comprising a
front suspension structure coupled to the first side member
adjacent to an intersection of the first side member and the first
cross-member; a front wheel supported by the front suspension
structure for rotational movement; and a stop structure rigidly
fixed to the first side member at a location rearward of the
intersection of the first side member and the first cross-member
and rearward of the front wheel.
8. The vehicle structure according to claim 7, wherein the
off-center impact reinforcement structure is further configured
such that during a second stage of the off-center impact event
immediately after the initial stage of the off-center impact event,
a rear surface of the push arm contacts the vehicle frame at the
intersection of the first side member and the first cross-member
and pivots about the intersection of the first side member and the
first cross-member such that the a front surface of the push arm
moves in a laterally outboard direction away from the first side
member and also moves in a rearward direction toward the front
wheel.
9. The vehicle structure according to claim 8, wherein the
off-center impact reinforcement structure is further configured
such that during the second stage of the off-center impact event
impacting forces acting on the push arm urge the vehicle frame to
move in a lateral direction away from the stationary barrier.
10. The vehicle structure according to claim 8, wherein the
off-center impact reinforcement structure is further configured
such that during a third stage of the off-center impact event after
the second stage, impacting forces from the stationary barrier
acting on the front wheel cause deformation of at least one of the
first side member and the front suspension structure.
11. The vehicle structure according to claim 10, wherein the
off-center impact reinforcement structure is further configured
such that during the third stage of the off-center impact event
after impacting forces cause deformation of at least one of the
first side member and the front suspension structure, the impacting
forces further urge the front wheel into contact with the stop
structure.
12. The vehicle structure according to claim 10, wherein the
off-center impact reinforcement structure is further configured
such that during the third stage of the off-center impact event
after impacting forces cause urge the front wheel into contact with
the stop structure, the impacting forces further urge the vehicle
frame to move rearward and laterally away from the stationary
barrier.
13. The vehicle structure according to claim 1, wherein the
off-center impact reinforcement structure is further configured
such that during the initial stage of the off-center impact event
against the front surface of the push arm, impacting forces from
the off-center impact event urge the push arm to undergo limited
movement rearward relative to the intersection of the first side
member and the first cross-member.
14. The vehicle structure according to claim 13, wherein the first
diagonal structure is coupled to a mid-portion of the second
cross-member, and the off-center impact reinforcement structure is
further configured such that during the initial stage of the
off-center impact event against the front surface of the push arm,
impacting forces from the push arm against the intersection of the
first side member and the first cross-member urge the first
diagonal structure to undergo limited movement relative to
mid-portion of the second cross-member.
15. The vehicle structure according to claim 14, further comprising
a second diagonal structure extending from a mid-portion of the
second cross-member rearward to a section of the second side member
rearward of the second cross-member, and the first diagonal
structure extends rearward to the mid-portion of the second
cross-member forward of the second diagonal structure.
16. The vehicle structure according to claim 15, wherein the
off-center impact reinforcement structure is further configured
such that during the initial stage of the off-center impact event
against the front surface of the push arm, impacting forces from
the off-center impact event are further transferred from the
mid-portion of the diagonal structure to an area of the second side
member rearward of the second cross-member.
17. The vehicle structure according to claim 16, wherein the
off-center impact reinforcement structure is further configured
such that during the initial stage of the off-center impact event,
impacting forces from the second cross-member to the second
diagonal structure cause the second cross-member to undergo limited
movement relative to the second diagonal structure.
18. The vehicle structure according to claim 17, wherein the
off-center impact reinforcement structure is further configured
such that during the initial stage of the off-center impact event,
impacting forces from second diagonal structure to the second side
member cause the second diagonal structure to undergo limited
movement relative to the second side member.
19. The vehicle structure according to claim 1, wherein the push
arm is configured to pivot about an area proximate the intersection
of the first side member and the first cross-member in response to
the off-center impact event.
Description
BACKGROUND
Field of the Invention
[0001] The present invention generally relates to a vehicle
structure. More specifically, the present invention relates to an
off-center support structure attached to portions of a vehicle
frame that responds to and absorbs impact force during an
off-center impact test.
Background Information
[0002] Vehicle structures are routinely being redesigned to include
structural features that absorb impact forces in response to impact
events. Recently introduced impact event tests include an
off-center impact test (also referred to as a small overlap test)
where a vehicle is provided with velocity in a vehicle longitudinal
direction (forward momentum) such that a front corner of the
vehicle (approximately 25 percent of the overall width of the
vehicle) impacts a fixed, rigid barrier. FIGS. 1, 2 and 3
schematically show an example of a conventional vehicle V
undergoing an impact event with a fixed barrier B in accordance
with the off-center impact test.
[0003] FIG. 1 shows the conventional vehicle V approaching the
rigid barrier B in the off-center impact test. FIG. 2 shows the
conventional vehicle V just after initial impact with the rigid
barrier B showing initial deformation and forward momentum being
transformed into rotational displacement about the rigid barrier B.
FIG. 3 shows the conventional vehicle V undergoing further
deformation and rotation as a result of the impact event.
SUMMARY
[0004] One object of the disclosure is to provide a vehicle frame
with additional structural elements that absorb and redirect impact
energy during an off-center impact test.
[0005] In view of the state of the known technology, one aspect of
the present disclosure is to provide a vehicle structure with a
vehicle frame and an off-center impact reinforcement structure. The
vehicle frame has a first side member, a second side member, a
first cross-member and a second cross-member, the first side member
and a second side member extending from a front portion of the
vehicle frame to a rear portion of the vehicle frame. The first
cross-member extends in a vehicle lateral direction and is rigidly
fixed to front areas of each of the first side member and the
second side member. The second cross-member extends in the vehicle
lateral direction and is rigidly fixed to areas of each of the
first side member and the second side member rearward from the
first cross-member defining an engine receiving space between the
first and second cross-members and the first and second side
members. The off-center impact reinforcement structure includes a
push arm and a first diagonal structure. The push arm is coupled to
the vehicle frame proximate an intersection of the first side
member and the first cross-member and extends in a forward and
laterally outboard direction from the intersection of the first
side member and the first cross-member. The first diagonal
structure extends rearward and laterally inboard from proximate the
intersection of the first side member and the first cross-member
toward a section of the second side member rearward of the first
cross-member. The off-center impact reinforcement structure is
configured such that during an initial stage of an off-center
impact event in which a stationary barrier impacts against a front
surface of the push arm during forward movement of the vehicle
frame, impacting forces from the off-center impact event are
transferred through the push arm to the vehicle frame at the
intersection of the first side member and the first cross-member,
and further from the intersection of the first side member and the
first cross-member to the first diagonal structure.
BRIEF DESCRIPTION OF THE DRAWINGS
[0006] Referring now to the attached drawings which form a part of
this original disclosure:
[0007] FIG. 1 is a schematic view of a conventional moving vehicle
showing its response to a small overlap test where a front corner
of the vehicle is aligned with a fixed, rigid barrier for eventual
impact with the barrier;
[0008] FIG. 2 is another schematic view of the conventional vehicle
showing its response to the small overlap test at the beginning of
an impact event with the front corner of the conventional vehicle
impacting the barrier and beginning to undergo deformation;
[0009] FIG. 3 is still another schematic view of the conventional
vehicle showing its response to the small overlap test with the
conventional vehicle undergoing further deformation during the
impact event;
[0010] FIG. 4 is a schematic view of a moving vehicle being
subjected to a small overlap test where approximately 25 percent of
the front of the vehicle aligned with a fixed, rigid barrier for
eventual impact with the barrier in accordance with an
embodiment;
[0011] FIG. 5 is another schematic view of the vehicle depicted in
FIG. 4 showing an initial response to the impact event of the small
overlap test with a front corner of the vehicle impacting the
barrier and beginning to undergo deformation in accordance with the
embodiment;
[0012] FIG. 6 is still another schematic view of the vehicle
depicted in FIGS. 4 and 5 showing a subsequent response to the
impact event of the small overlap test with the moving vehicle
undergoing further deformation during the impact event in
accordance with the embodiment;
[0013] FIG. 7 is a perspective view of the vehicle having an
off-center impact reinforcement structure 12 in accordance with the
embodiment;
[0014] FIG. 8 is a bottom view (looking upward) of a frame from the
vehicle depicted in FIG. 7, but with the off-center impact
reinforcement structure removed, showing a first side member, a
second side member, a first cross-member and a second cross-member
of the frame in accordance with the embodiment;
[0015] FIG. 9 is another bottom view (looking upward) of a portion
of the frame depicted in FIG. 8, but with the off-center impact
reinforcement structure installed to the frame, showing a push arm
assembly, a first structure (a first diagonal structure), a
secondary reinforcement cross-member, a second structure (a second
diagonal structure), a gap maintaining structure, a bulkhead
structure and a stop structure of the off-center impact
reinforcement structure in accordance with the embodiment;
[0016] FIG. 10 is a perspective view of a driver's front side of
the frame and the off-center impact reinforcement structure,
showing details of the push arm assembly in accordance with the
embodiment;
[0017] FIG. 11 is another perspective view showing an underside of
the frame and the off-center impact reinforcement structure,
showing details of the push arm assembly, the first structure and
the second structure in accordance with the embodiment;
[0018] FIG. 12 is an exploded view of a portion of the frame and
the off-center impact reinforcement structure, showing the various
elements of the push arm assembly as depicted in FIG. 11, including
a front plate, a main body, a pivot bracket, a energy absorbing
structure and a support bracket in accordance with the
embodiment;
[0019] FIG. 13 is a side view the driver's front side of the frame
and the off-center impact reinforcement structure, showing details
of the push arm assembly in accordance with the embodiment;
[0020] FIG. 14 is another perspective view showing an upper side of
the frame and the off-center impact reinforcement structure,
showing details of the push arm assembly in accordance with the
embodiment;
[0021] FIG. 15 is a bottom view of a front portion of the frame and
portions of the off-center impact reinforcement structure, showing
the push arm assembly, the first structure and the secondary
reinforcement cross-member in accordance with the embodiment;
[0022] FIG. 16 is a perspective view of a portion the driver's
front side of the frame and the off-center impact reinforcement
structure, showing details of the push arm assembly and an
intersection of the first side member and the first cross-member in
accordance with the embodiment;
[0023] FIG. 17 is a perspective view showing an upper side of the
frame and the off-center impact reinforcement structure, showing
details of the push arm assembly and the secondary reinforcement
cross-member 74 in accordance with the embodiment;
[0024] FIG. 18 is a bottom view of a front portion of driver's side
of the frame and portions of the off-center impact reinforcement
structure, showing details of the push arm assembly in accordance
with the embodiment;
[0025] FIG. 19 is another bottom view of the front portion of the
frame and portions of the off-center impact reinforcement
structure, showing the push arm assembly and the first structure
with the support bracket installed to the push arm assembly in
accordance with the embodiment;
[0026] FIG. 20 is another bottom view of the front portion of the
frame and portions of the off-center impact reinforcement
structure, showing the push arm assembly with the support bracket
removed showing the pivot bracket and the energy absorbing
structure in accordance with the embodiment;
[0027] FIG. 21 is a top view of the front portion of the off-center
impact reinforcement structure, showing the pivot bracket and the
energy absorbing structure of the push arm assembly in accordance
with the embodiment;
[0028] FIG. 22 is a top perspective view of the front portion of
the off-center impact reinforcement structure, showing the pivot
bracket and the energy absorbing structure of the push arm assembly
in accordance with the embodiment;
[0029] FIG. 23 is a bottom view of a portion of the push arm
assembly showing the support bracket in accordance with the
embodiment;
[0030] FIG. 24 is a bottom view of the front portion of the frame
and portions of the off-center impact reinforcement structure,
showing the push arm assembly and the first structure with the
support bracket and a bracket of the first structure in phantom
showing the pivot bracket, the energy absorbing structure and a gap
defined between the first cross-member and a beam of the first
structure in accordance with the embodiment;
[0031] FIG. 25 is another bottom view of the front portion of the
frame and portions of the off-center impact reinforcement
structure, showing the push arm assembly with the support bracket,
the pivot bracket and the energy absorbing structure removed
showing vehicle suspension structures otherwise concealed by the
push arm assembly in accordance with the embodiment;
[0032] FIG. 26 is a bottom view of a front portion of the vehicle
including the frame and off-center impact reinforcement structure
during an initial stage of an impact event where the push arm
assembly initially makes contact with a fixed barrier in accordance
with the embodiment;
[0033] FIG. 27 is another bottom view of the front portion of the
vehicle similar to FIG. 26 showing the frame and off-center impact
reinforcement structure during a second stage of the impact event
where the push arm assembly begins to deform and undergo pivoting
movement in accordance with the embodiment;
[0034] FIG. 28 is another bottom view of the front portion of the
vehicle similar to FIGS. 26 and 27 showing the frame and off-center
impact reinforcement structure during a third stage of the impact
event where the push arm assembly continues to deform and undergo
pivoting movement in accordance with the embodiment;
[0035] FIG. 29 is a bottom view of a front portion of the push arm
assembly of the off-center impact reinforcement structure with the
support bracket removed showing the energy absorbing structure and
pivot bracket prior to the impact event depicted in FIGS. 26-28, in
accordance with the embodiment;
[0036] FIG. 30 is another bottom view of the front portion of the
push arm assembly with the support bracket removed showing the
energy absorbing structure and pivot bracket during an initial
stage of the impact event depicted in FIGS. 26-28, in accordance
with the embodiment;
[0037] FIG. 31 is another bottom view of the front portion of the
push arm assembly with the support bracket removed showing the
energy absorbing structure and pivot bracket during a second stage
of the impact event depicted in FIGS. 26-28, in accordance with the
embodiment;
[0038] FIG. 32 is another bottom view of the front portion of the
push arm assembly with the support bracket removed showing the
energy absorbing structure and pivot bracket during a final stage
of the impact event depicted in FIGS. 26-28, in accordance with the
embodiment;
[0039] FIG. 33 is another bottom view of the front portion of the
frame and the off-center impact reinforcement structure showing the
push arm assembly and the first structure with the support bracket
and the bracket of the first structure in phantom showing the
energy absorbing structure and pivot bracket after the impact event
depicted in FIGS. 26-28, in accordance with the embodiment;
[0040] FIG. 34 is a front perspective view of the frame and the
off-center impact reinforcement structure with portions thereof cut
away showing the secondary reinforcement cross-member in accordance
with the embodiment;
[0041] FIG. 35 is another bottom view of a mid-vehicle portion of
the frame and the off-center impact reinforcement structure showing
the first structure, the secondary reinforcement cross-member, the
second structure, the gap maintaining structure and the stop
structure in accordance with the embodiment;
[0042] FIG. 36 is a top view of the gap maintaining structure
showing details of an upper attachment bracket fixed to the second
cross-member, a first lower attachment bracket and a second lower
attachment bracket in accordance with the embodiment;
[0043] FIG. 37 is a perspective bottom view of the mid-vehicle
portion of the frame and the off-center impact reinforcement
structure showing the first structure, the secondary reinforcement
cross-member, the second structure and the gap maintaining
structure in accordance with the embodiment;
[0044] FIG. 38 is a perspective view of the first structure and the
secondary reinforcement cross-member shown removed from the frame
and the off-center impact reinforcement structure in accordance
with the embodiment;
[0045] FIG. 39 is an exploded view of portions of the frame
including the second cross-member, the first structure, the second
structure and portions of the gap maintaining structure in
accordance with the embodiment;
[0046] FIG. 40 is a perspective view of the first lower attachment
bracket of the gap maintaining structure shown removed from the
vehicle in accordance with the embodiment;
[0047] FIG. 41 is an exploded perspective view of the first lower
attachment bracket of the gap maintaining structure shown removed
from the vehicle in accordance with the embodiment;
[0048] FIG. 42 is an exploded perspective view of the second
cross-member showing details of a bulkhead within the second
cross-member in accordance with the embodiment;
[0049] FIG. 43 is a perspective view of the second cross-member
showing further details of the bulkhead within the second
cross-member in accordance with the embodiment;
[0050] FIG. 44 is another exploded perspective view of the second
cross-member showing details of the bulkhead in accordance with the
embodiment;
[0051] FIG. 45 is a perspective top view of the second cross-member
showing an upper surface of the upper attachment bracket and the
first lower attachment bracket in accordance with the
embodiment;
[0052] FIG. 46 is a perspective bottom view of a portion of the
second side member of the frame and features of a the second
structure coupled thereto in accordance with the embodiment;
[0053] FIG. 47 is another perspective bottom view of another
portion of a rear portion of the second side member of the frame
and features of a rear attachment portion of the second structure
with one of the brackets in phantom revealing details of a stop
bracket in accordance with the embodiment;
[0054] FIG. 48 is a perspective view of brackets of the rear
attachment portion shown removed from the second side member and
the second structure in accordance with the embodiment;
[0055] FIG. 49 is another perspective view of two of the brackets
of the rear attachment portion shown removed from the second side
member and the second structure in accordance with the
embodiment;
[0056] FIG. 50 is an exploded perspective view of two of the
brackets of the rear attachment portion depicted in FIG. 49 in
accordance with the embodiment;
[0057] FIG. 51 is an exploded perspective view of a portion of the
second structure shown removed from the second side member, showing
a hollow beam and an end plate thereof in accordance with the
embodiment;
[0058] FIG. 52 is a top view of the hollow beam and the end plate
depicted in FIG. 51 in accordance with the embodiment;
[0059] FIG. 53 is a perspective bottom view of the second
cross-member and the upper attachment bracket with the hollow beam
removed showing recessed areas and fasteners of the upper
attachment bracket in accordance with the embodiment;
[0060] FIG. 54 is a bottom view of a portion of the second
cross-section and the hollow beam of the second structure in
accordance with the embodiment;
[0061] FIG. 55 is a bottom perspective view of a secondary diagonal
structure and a corresponding rear attachment structure coupled to
the first side member in accordance with the embodiment;
[0062] FIG. 56 an exploded perspective view of the secondary
diagonal structure and the corresponding rear attachment structure
depicted in FIG. 55 in accordance with the embodiment;
[0063] FIG. 57 is a perspective side view of the first side member
of the frame showing the stop structure fixed thereto in accordance
with the embodiment;
[0064] FIG. 58 is another perspective side view similar to FIG. 57,
showing the stop structure with an outer plate removed showing
various plate members that define the stop member in accordance
with the embodiment; and
[0065] FIG. 59 is a bottom view of the frame and the off-center
impact reinforcement structure during an impact event where the
front wheel has moved into contact with the stop structure.
DETAILED DESCRIPTION OF EMBODIMENTS
[0066] Selected embodiments will now be explained with reference to
the drawings. It will be apparent to those skilled in the art from
this disclosure that the following descriptions of the embodiments
are provided for illustration only and not for the purpose of
limiting the invention as defined by the appended claims and their
equivalents.
[0067] Referring initially to FIG. 4-9, a vehicle 10 is illustrated
in accordance with a first embodiment. The vehicle 10 is provided
with an off-center impact reinforcement structure 12 (shown in FIG.
9) that is configured to absorb and re-direct forces during an
impact event such as an off-center impact test (also referred to as
a small overlap test) described further below.
[0068] The Insurance Institute for Highway Safety (IIHS) has
developed various tests where vehicles are provided with forward
velocity and impacted against fixed, rigid barriers, like the rigid
barrier B depicted in FIGS. 1-3. In the IIHS offset tests, the
conventional vehicle C is aimed at the rigid barrier B such that
approximately 25 percent of the front area of the conventional
vehicle C impacts the rigid barrier B. In other words, as indicated
in FIGS. 1-3, only a front corner of the conventional vehicle C
impacts the rigid barrier B. This IIHS test is also known as a
frontal offset, narrow offset, or small overlap test. In such
tests, a front bumper assembly of the conventional vehicle C is
either not impacted, or undergoes only limited contact with the
rigid barrier B during the impact event. Therefore, other
structures at the front of the conventional vehicle C impact the
rigid barrier B and absorb at least some of the kinetic energy
associated with the rapid deceleration of the vehicle C that
results from the impact event. When the vehicle C is provided with
velocity and impacts the rigid barrier B, the rapid deceleration of
the vehicle C transforms the kinetic energy associated with the
mass and velocity of the vehicle C into deformation of the vehicle
C and counter movement of the vehicle C. As is well known, kinetic
energy is a function of mass times velocity. During the small
offset test, the kinetic energy of the vehicle C is partially
absorbed and partially transformed into other forms of kinetic
energy, such as rotary motion. It should be understood that the
kinetic energy associated with the forward velocity of the vehicle
C (and in the description below) is transformed into an impacting
force upon impact due to the rapid deceleration of the vehicle C.
Consequently, hereinbelow, the terms impact force and impacting
force as used herein correspond to the kinetic energy applied to
the vehicle 10 during the small overlap test (the impact event), as
described below with respect to the various embodiments.
[0069] The test developed by the IIHS is represented schematically
in FIGS. 1-3. During the impact event, a variety of structures
undergo deformation. This deformation is not explicitly depicted in
FIGS. 2 and 3 with any degree of accuracy because such deformation
varies from conventional vehicle to conventional vehicle, depending
upon the overall design of the front structure of the conventional
vehicle C. Instead, in FIG. 3, the conventional vehicle C is
depicted with a generic degree of deformation as a result of the
impact event. However, the conventional vehicles tested by the IIHS
using the small overlap test have a relatively consistent response
in that during the impact event with the rigid barrier B, the rear
end R of the conventional vehicle C undergoes some rotation and
swings laterally away from the rigid barrier B, as indicated in
FIG. 3.
[0070] In other words, the forward velocity F.sub.F of the
conventional vehicle C as it moves is transformed upon impact with
the rigid barrier B. The velocity F.sub.F results in an equal and
opposite reaction force acting on the vehicle C as the vehicle C
suddenly decelerates. It is desirable to move the vehicle laterally
outward from the barrier and avoid unnecessary loading of the
dash-wall and/or A-pillar.
[0071] The force directing features of the off-center impact
reinforcement structure 12 of the vehicle 10 as described
hereinbelow are such that during an impact event (such as a small
overlap test), the impact forces are absorbed and transmitted to
various structures within the vehicle 10, as shown in FIGS. 4, 5
and 6. Specifically, in FIG. 4 the vehicle 10 is provided with a
forward velocity V.sub.F1 and is subjected to a small overlap test
where approximately 25 percent of the front of the vehicle is
aligned with the rigid barrier B. In FIG. 5 the vehicle 10
undergoes an initial response to the impact event of the small
overlap test with a front corner of the vehicle impacting the
barrier and beginning to undergo deformation. Hence, the forward
velocity V.sub.F1 is reduced to a velocity V.sub.F2 with some of
the impact energy causing the vehicle 10 to move laterally with a
velocity V.sub.L1, as shown in FIG. 5. In FIG. 6, the vehicle 10
undergoes a subsequent response to the impact event in that one or
more of the features of the off-center impact reinforcement
structure 12 has functioned properly and caused the vehicle 10 to
move laterally with the forward velocity V.sub.F2 is reduced to a
velocity V.sub.F3 and a lateral velocity V.sub.L2 that is greater
than the V.sub.L1. In other words, the off-center impact
reinforcement structure 12 is configured to absorb impact energy
and direct that force to various portions of the vehicle, and the
off-center impact reinforcement structure 12 is also configured to
move the vehicle 10 in a lateral direction away from the barrier
B.
[0072] It should be understood from the drawings and the
description herein, that during an impact event, such as the small
overlap test, the reaction forces experienced by the vehicle 10 as
it impacts the rigid barrier B are significant. These significant
reaction forces are exponentially greater than the forces the
structures of the vehicle 10 undergo during normal operating usage
of the vehicle 10. In other words, the impact events referred to
herein are intended as destructive tests. Further, the impact
events of the small overlap tests are configured such that the
vehicle 10 impacts the rigid barrier B at portions of the vehicle
10 outboard of some of the vehicle's structures (not a central area
of the vehicle 10), as described in greater detail below.
[0073] In the various embodiments described below, the vehicle 10
includes combinations of features of the off-center impact
reinforcement structure 12 shown in FIG. 9 and described further
below.
[0074] FIG. 7 shows one embodiment of the vehicle 10. In FIG. 7,
the vehicle 10 is depicted as a pickup truck that includes a body
structure 14 that defines, for example. an engine compartment 16, a
passenger compartment 18 and a cargo area 20. The body structure 14
is installed to and rests on a frame 22. The frame 22 is shown
removed from the vehicle 10 in FIGS. 8 and 9. Specifically, FIG. 8
shows only the frame 22 with the off-center impact reinforcement
structure 12 removed, and FIG. 9 shows the frame 22 with the
off-center impact reinforcement structure 12 installed thereto.
[0075] In FIG. 7, the depicted pickup truck that defines the
vehicle 10 is a heavy duty vehicle intended to haul large and/or
heavy materials. The frame 22 is therefore a rigid, strong
structure able to withstand heavy duty usage. However, it should be
understood from the drawings and the description herein, that the
frame 22 and the off-center impact reinforcement structure 12
described below can be configured for smaller vehicles or larger
vehicles and is not limited to usage in a heavy duty vehicle such
as the vehicle 10. In other words, the off-center impact
reinforcement structure 12 can be used on any size vehicle that
includes a frame such as the frame 22 where the body structure 14
attaches to and is supported by the frame 22. It should also be
understood from the drawings and description, that the off-center
impact reinforcement structure 12 can also be employed with a
unibody vehicle. A unibody vehicle is a vehicle that does not
typically includes a separate frame such as the frame 22. Rather,
the unibody vehicle includes various structural elements welded
together. Elements of the unibody vehicle serve as frame elements
functionally equivalent to the elements of the frame 22. For
example, U.S. Pat. No. 8,870,267 assigned to Nissan North America,
discloses a unibody vehicle body structure. The front structural
support portions (30) disclosed in U.S. Pat. No. 8,870,267 are
basically vehicle side members, such as those of the frame 22
(described in greater detail below). U.S. Pat. No. 9,180,913, also
assigned to Nissan North America, also discloses a unibody vehicle
body structure and further discloses an engine cradle. The elements
of the off-center impact reinforcement structure 12 can be
installed to portions of the unibody vehicle disclosed in U.S. Pat.
No. 8,870,267 and portions of the engine cradle of U.S. Pat. No.
8,870,267. Both U.S. Pat. No. 8,870,267 and U.S. Pat. No. 9,180,913
are incorporated herein by reference in their entirety. Since
unibody vehicles are conventional structures, further description
is omitted for the sake of brevity.
[0076] For clarity, the off-center impact reinforcement structure
12 has also been removed from the frame 22 in FIG. 8. The
off-center impact reinforcement structure 12 is shown in FIG. 9
installed to specific portions of the frame 22.
[0077] In FIG. 8 several directions relative to the frame 22 (and
the vehicle 10) are shown in order to define orientations of the
various features of the vehicle 10 and the off-center impact
reinforcement structure 12. Specifically, the vehicle 10 and the
frame 22 define a longitudinal center line C.sub.L that extends in
a lengthwise direction of the vehicle 10 along a central portion of
the vehicle 10. At a left-hand side of FIG. 8, a forward direction
FD is indicated by the depicted arrow, and at a right-hand side of
FIG. 8 a rearward direction R.sub.D is indicated by the depicted
arrow. As well, inboard directions I.sub.D and outboard directions
O.sub.D relative to the longitudinal center line C.sub.L are also
shown in FIG. 8.
[0078] As shown in FIG. 8, the frame 22 includes a first side
member 30, a second side member 32, a first cross-member 34, a
second cross-member 36 and a third cross-member 38 and an optional
front cross-member 40. FIG. 8 shows an underside of the frame 22.
In other words, the depiction of the frame 22 is taken from below
the frame 22 looking upward. The frame 22 is made of heavy gauge
steel, but can alternatively be made of other materials depending
upon the overall design of the vehicle 10. It should therefore be
understood that the first side member 30 extends along and under a
driver's side of the vehicle 10, and the second side member 32
extends along and under a passenger's side of the vehicle 10.
[0079] The first side member 30 is an elongated beam (a first side
member) that has multiple contours and shapes. Specifically, the
first side member 30 has a front end 30a and a rear end 30b. The
first side member 30 also has a first portion 30c, a second portion
30d and a third portion 30e. The first portion 30c extends in the
rearward direction R.sub.D from the front end 30a to a location
proximate the second cross-member 36. The first portion 30c is
generally straight. The second portion 30d has a curved shape such
that just rearward of the first portion 30c, the second portion 30d
gradually curves in the outboard direction O.sub.D. The third
portion 30e is generally straight, but can include contours and
curves, depending upon the overall design of the vehicle 10.
[0080] Similarly, the second side member 32 is an elongated beam (a
second side member) that has multiple contours and shapes that are
symmetrical to the first side member 30. Specifically, the second
side member 32 has a front end 32a and a rear end 32b. The second
side member 32 also has a first portion 32c, a second portion 32d
and a third portion 32e. The first portion 32c extends in the
rearward direction R.sub.D from the front end 32a to a location
proximate the second cross-member 36. The first portion 32c is
generally straight. The second portion 32d has a curved shape such
that just rearward of the first portion 32c, the second portion 32d
gradually curves in the outboard direction O.sub.D.
[0081] The first portions 30c and 32c of the first and second side
members 30 and 32 are a first distance away from one another, and
the third portions 30e and 32e are a second distance away from one
another, with the second distance being greater than the first
distance.
[0082] The first and second side members 30 and 32 each include
vehicle body attachment flanges 42 and 44 (cabin attachment
flanges). The attachment flanges 42 and 44 are welded to the first
and second side members 30 and 32 and are dimensioned and shaped to
attach to the body structure 14 of the vehicle 10. The attachment
flanges 42 extend from outboard sides of the first portions 30c and
32c of the first and second side members 30 and 32 forward of the
first cross-member 34. The attachment flanges 44 extend from
outboard sides of the second portions 30d and 32d of the first and
second side members 30 and 32 rearward of the second cross-member
36.
[0083] Although not shown in FIG. 8, the third portions 30e and 32e
of the first and second side members 30 and 32 can also include
body attachment flanges configured for attachment to structures
that define the cargo area 20 of the vehicle 10. Further, the third
portions 30e and 32e can be at the same level above the ground as
the first portions 30c and 32c, or can be raised above the ground
at a level higher that the first portions 30c and 32c, with the
second portions 30d and 32d including an upward curvature.
[0084] As shown in FIG. 8, each of the first portions 30c and 32c
of the first and second side members 30 and 32 further include
front suspension structures such as coil spring supports 46, first
suspension structures 48 and second suspension structures 50.
[0085] The coil spring supports 46 are rigidly fixed (i.e. welded)
to respective ones of the first and second side members 30 and 32.
The coil spring supports 46 are dimensioned and shaped to support
lower ends of front suspension coil springs in a conventional
manner. Since front suspension coil springs are conventional
structures, further description is omitted for the sake of
brevity.
[0086] The first suspension structures 48 are defined by pairs of
flanges welded to lower surfaces of the first and second side
members 30 and 32. Similarly, the second suspension structures 50
are defined by pairs of flanges welded to lower surfaces of the
first and second side members 30 and 32 rearward and spaced apart
from the first suspension structures 48. The first suspension
structures 48 are adjacent to or aligned with the first
cross-member 34. The second suspension structures 50 are adjacent
to or aligned with the second cross-member 36.
[0087] The first suspension structures 48 and the second suspension
structures 50 are configured to support a lower control arm 52 for
pivotal movement about pivot bolts 54. The lower control arm 52 is
part of the steering and suspension structure of the vehicle 10.
Since steering and suspension structures (and, in particular,
control arm structures) are conventional vehicle components,
further description is omitted for the sake of brevity.
[0088] The engine compartment 16 of the body structure 14 is
approximately located in the space above and between the first
portions 30c and 32c of the first and second side members 30 and
32. A front portion of the passenger compartment 18 is located in
the space above and between the second portions 30d and 32d of the
first and second side member rearward of the engine compartment 16.
The remainder of the passenger compartment 18 and the cargo area 20
of the body structure 14 are located above the third portions 30e
and 32e of the first and second side members 30 and 32.
[0089] As shown in FIGS. 9, 10, 13, 14 and 16, the first
cross-member 34 is rigidly attached to the first side member 30 and
rigidly attached to the second side member 32. The first
cross-member 34 can be co-planar with the first and second side
members 30 and 32, or can be located above or below the first and
second side members 30 and 32. However, in the depicted embodiment
the first cross-member 34 is located below the first and second
side members 30 and 32.
[0090] The first cross-member 34 has a first end 34a, a second end
34b and mid-section 34c that extends from the first end 34a to the
second end 34b. The first end 34a of the first cross-member is
fixed to the first side member 30 via a plurality of reinforcement
brackets 60, 62 and 64 shown in FIGS. 10, 13, 14 and 16. The
reinforcement brackets 60, 62 and 64 have differing surfaces, with
some of those surfaces being welded to the first side member 30 and
some of those surfaces, such as surfaces 60a, 60b and 60c,
extending downward with the reinforcement brackets 60, 62 and 64
being welded to the first end 34a of the first cross-member 34
along or below the surfaces 60a, 62a and 64a. The reinforcement
brackets 60, 62 and 64 are considered to be part of the first
cross-member 34, but can also be considered part of the first side
member 30. The reinforcement brackets 60, 62 and 64, along with the
first side member 30 and the first cross-member 34 define an
intersection 66 of the first side member 30 and the first
cross-member 34.
[0091] In the depicted embodiment, the first cross-member 34
extends in a vehicle lateral direction from the first portion 30c
of the first side member 30 to the first portion 32c of the second
side member 30 at a location rearward of the front ends 30a and
32a. The first cross-member is further rigidly fixed to each of the
first side member 30 and the second side member 32. As shown in
FIGS. 8 and 9, the first cross-member 34 extends perpendicular to
the first portion 30c of the first side member 30 and the first
portion 32c of the second side member 32.
[0092] As shown in FIGS. 13 and 14, an upper surface 34d of the
mid-section 34c of the first cross-member 34 is vertically spaced
apart from an upper surface 30f of the first side member 30 (the
first side member) in the area of the first portion 30c.
Specifically, the upper surface 34d of the mid-section 34c of the
first cross-member 34 is below the upper surface 30f of the first
side member 30 in the area of the first portion 30c. As shown in
FIG. 13, the upper surface of the first side member 30 defines a
plane P.sub.1. The upper surface 34d of the mid-section 34c of the
first cross-member 34 extends along a plane P.sub.2. As shown in
FIG. 13, the plane P.sub.1 is vertically above the plane
P.sub.2.
[0093] The second end 34b of the first cross-member 34 is also
fixed to the second side member 32 in a manner consistent with the
attachment of the first end 34a to the first side member 30. Since
the attachment of the second end 34b to the second side member 32
is basically the same as the attachment of the first end 34a to the
first side member 30, further description of the attachment of the
first cross-member 34 to the second side member 32 is omitted for
the sake of brevity.
[0094] The second cross-member 36 extends in the vehicle lateral
direction and is rigidly fixed to areas of each of the first side
member 30 and the second side member 32 rearward of the first
cross-member 34. The second cross-member 36 can be welded to each
of the first portions 30c and 32c of the first and second side
members 30 and 32. However, as is described below with reference to
FIGS. 37, 39 and 42, the second cross-member 36 can be attached to
the first and second side members 30 and 32 via mechanical
fasteners (not shown). Further, the second cross-member 36 is
vertically aligned with the first portions 30c and 32c of the first
and second side members 30 and 32 and extends in a direction
perpendicular to each of the first and second side members 30 and
32. The second cross-member 36 is also parallel to the first
cross-member 34.
[0095] An engine receiving space is defined in the area confined
between the first and second cross-members 30 and 32, and between
the first and second side members 34 and 36.
[0096] The third cross-member 38 extends between forward ends of
each of the third portions 30e and 32e of the first and second side
members 30 and 32. The third cross-member 38 is welded to each of
the first and second side members 30 and 32 and can serve as an
attachment structure for a rear portion of the body structure 14
(at a mid-portion of the passenger compartment 18), and/or can
serve as an attachment structure for the structure that defines the
cargo area 20.
[0097] The optional front cross-member 40 is welded or otherwise
rigidly fixed to the front ends 30a and 32a of the first and second
side members 30 and 32. A bumper structure (not shown) can be
attached to the optional front cross-member 40. Alternatively, the
bumper structure (not shown) can be attached to the front ends 30a
and 32a of the first and second side members 30 and 32 replacing
the optional front cross-member 40.
[0098] A description of the off-center impact reinforcement
structure 12 is now provided with specific reference to FIGS.
9-60.
[0099] With initial reference to FIG. 9, the off-center impact
reinforcement structure 12 basically includes a push arm assembly
70, a first structure 72 (a first diagonal structure), a secondary
reinforcement cross-member 74, a second structure 76 (a second
diagonal structure), a gap maintaining structure 78, a bulkhead
structure 80 (shown in FIGS. 36 and 42-44) and a stop structure 82
(a tire catching structure). Each of the push arm assembly 70, the
first structure 72, the secondary reinforcement cross-member 74,
the second structure 76, the gap maintaining structure 78, the
bulkhead structure 80 and the stop structure 82 is described
separately below. In the depicted embodiment, the off-center
reinforcement structure 12 is installed to the vehicle 10 with the
push arm assembly 70 installed to a driver's side of the vehicle 10
with the first and second structures 70 and 72 extending rearward
and laterally toward the passenger's side of the vehicle 10.
However, it should be understood from the drawings and the
description herein that the off-center reinforcement structure 12
can be installed with the push arm assembly 70 installed to the
passenger's side of the vehicle 10, or, alternatively two of the
off-center reinforcement structures 12 can be incorporated into the
vehicle 10 with one the push arm assembly 70 being installed at
each of the driver's side and the passenger's side of the vehicle
10.
[0100] As shown in FIGS. 9-34, the push arm assembly 70 is coupled
to the frame 22 (the vehicle frame) proximate the intersection 66
of the first side member 30 and the first cross-member 34. The push
arm assembly 70 extends in a forward and laterally outboard
direction from the intersection 66 of the first side member 30 and
the first cross-member 34. The push arm assembly 70 defines an
angle .alpha..sub.1 relative to the first portion 32c of the first
side member 30, as shown in FIGS. 9 and 10. The angle .alpha..sub.1
is between 25 and 45 degrees. In the depicted embodiment, the angle
.alpha..sub.1 is approximately 35 degrees.
[0101] As shown in an exploded view in FIG. 12, the push arm
assembly 70 basically includes a main body 90, a front end plate
92, a energy absorbing structure 94, a pivot bracket 96, a support
bracket 98 and an attachment bracket 100.
[0102] The main body 90 is a hollow elongated beam element having a
front end 90a and a rear end 90b. The front end 90a is shaped to
conform the front end plate 92 (described in greater detail below).
Specifically, the front end 90a has two portions that are angularly
offset from one another in correspondence with the shape of the
front end plate 92. The rear end 90b of the main body 90 has offset
end surfaces. Specifically, a lower portion 90c of the rear end 90b
of the main body 90 extends rearward and is formed with an angle
.alpha..sub.2 relative to a lengthwise direction of the main body
90 and an upper portion 90d is formed with an angle .alpha..sub.3
relative to a lengthwise direction of the main body 90. The purpose
of the lower portion 90c and the upper portion 90d is further
understood in the description of the pivot bracket 98, described
below.
[0103] The front end plate 92 of the push arm assembly 70 is
fixedly attached (for example, welded) to the front end 90a. The
front end plate 92 defines a front surface having a first section
92a and a second section 92b. In other words, the first and second
sections 92a and 92b together define the front surface of the front
end plate 92. The front end plate 92 (and the front end 90a of the
main body 90 of the push arm assembly 70) extends forward and
laterally outward such that the front surface (both the first
portion 92a and the second portion 92b) of the push arm assembly 70
is located laterally outboard of and spaced apart from the front
end 30a of the first side member 30.
[0104] The second section 92b of the front end plate 92 is located
between the first section 92a and the first side member 30.
Further, the second section 92b of the front end plate 92 is
located inboard of the first section 92a and extends forward of the
first section 92a. As shown in FIG. 9, the first section 92a of the
front end plate 92 extends in a direction perpendicular to a
lengthwise direction of the vehicle frame 22 in a non-impacted
state, where the lengthwise direction is parallel the longitudinal
center line C.sub.L of the vehicle 10. An obtuse angle
.alpha..sub.4 is defined between the first section 92a and the
second section 92b of the push arm assembly 70 is between 110 and
135 degrees. As shown in the FIG. 9, the obtuse angle .alpha..sub.4
is defined between the first section 92a and the second section 92b
of the front surface of the push arm is 125 degrees.
[0105] As shown in FIG. 20, the rear end 90a of the main body 90 is
spaced apart from the intersection 66 of first side member 30 and
the first cross-member 34 defining a gap G.sub.1 therebetween. More
specifically, the main body 90, the energy absorbing structure 94
and the pivot bracket 96 are all spaced apart (non-contacting) from
the intersection 66 of the first side member 30 and the first
cross-member 34.
[0106] As shown by comparing FIG. 20 (with the energy absorbing
structure 94 and the pivot bracket 96 removed) and FIG. 24 (with
the energy absorbing structure 94 and the pivot bracket 96
installed), the rear end 90a of the main body 90 is shaped to
receive the energy absorbing structure 94 and the pivot bracket 96.
More specifically, the energy absorbing structure 94 and the pivot
bracket 96 are located within the gap G.sub.1 with the vehicle 10
in a non-impacted state, and are spaced apart from the intersection
66.
[0107] As shown in FIGS. 12, 20-22 and 34, the energy absorbing
structure 94 includes a plurality of cup-shaped members including a
first cup-shaped member 104, a second cup-shaped member 106 and a
third cup-shaped member 108. The first, second and third cup-shaped
members 104, 106 and 108 can also be U-shaped members that are
nested within one another in a manner described below.
[0108] Specifically, at least the first and second cup-shaped
members 104 and 106 have similar conforming shapes. For instance,
the first cup-shaped member 104 has two side walls 104a and 104b,
and an end wall 104c that extends between the two side walls 104a
and 104b, thereby defining an overall U-shape as viewed in
cross-section in FIGS. 20 and 21. The second cup-shaped member 106
has two side walls 106a and 106b, and an end wall 106c that extends
between the two side walls 106a and 106b, thereby also defining an
overall U-shape. The third cup-shaped member 108 is shown as a flat
plate member in cross-section but can also have side walls (not
shown).
[0109] The first, second and third cup-shaped members 104, 106 and
108 are attached to one another such that the end wall 104c is
spaced apart from the end wall 106c, and the third cup-shaped
member 108 is further spaced apart from the end walls 104c and
106c, as shown in FIGS. 20, 21 and 22. Specifically, the side walls
104a and 104b of the first cup-shaped member 104 are fixedly
attached to the side walls 106a and 106b of the second cup-shaped
member 106 via welds W such the end walls 104c and 106c are spaced
apart from one another in the non-impacted state. The third
cup-shaped member 108 is fixed via welds W to inner surfaces of the
side walls 106a and 106b within the second cup-shaped member 106
such that the third cup-shaped member 108 being spaced apart from
the end wall 106c.
[0110] The pivot bracket 96 is attached to both the energy
absorbing structure 94 and the rear end 90b of the main body 90 via
welds W, as shown in FIG. 22. The pivot bracket 96 has an overall
triangular shape and is dimensioned to contact the lower portion
90c of the rear end 90b of the main body 90 of the push arm
assembly 70, and contact a lower surface of the upper portion 90d
of the rear end 90b of the main body 90 of the push arm assembly
70. Specifically, as shown in FIG. 20, a first edge 96a of the
pivot bracket 96 contacts an edge of the lower portion 90c of the
rear end 90b of the main body 90 of the push arm assembly 70. As
shown in FIG. 22, an upper surface 96b of the pivot bracket 96
contacts the upper portion 90d of the rear end 90b of the main body
90 of the push arm assembly 70 and is welded thereto. The upper
surface 96b also abuts the first cup-shaped member 104 of the
energy absorbing structure 94. The pivot bracket 96 also has a rear
surface 96c within the gap G.sub.1 that is spaced apart from the
intersection 66 and from the first cross-member 34 in the
non-impacted state. However, as is explained in greater detail
below, in response to an impact event, the rear surface 96c can
move into contact with the first cross-member 34.
[0111] As shown in FIG. 20 with the support bracket 98 removed, the
rear end 90b of the main body 90, the energy absorbing structure 94
and the pivot bracket 96 are all spaced apart from the pivot bolt
54 and the first suspension structure 48 in the non-impacted state.
As described in greater detail below, the support bracket 98 is
designed to be removable from the vehicle 10 in order to gain
access to the pivot bolt 54 in the event that steering adjustments
or repairs are need to the front suspension structures of the
vehicle 10.
[0112] Further, the pivot arm assembly 70, including the main body
90, the front end plate 92, the energy absorbing structure 94 and
the pivot bracket 96 can also be removed from the vehicle 10 for
servicing and easy access to mechanical components of the vehicle
10 that may be covered or partially covered by the pivot arm
assembly 70.
[0113] As shown in FIGS. 9, 11, 13-15 and 18-19, the support
bracket 98 is attached to the main body 90 of the push arm assembly
70 and first cross-member 34 via removable mechanical fasteners
F.sub.1. The support bracket 98 has a contoured shape. For example,
an underside surface 98a as viewed in FIGS. 10, 15, 18-19 and 23
gives the appearance that the support bracket 98 is generally flat.
However, as shown in perspective views in FIGS. 12-14, the support
bracket 98 has a truncated U-shape with side portions 98b and 98c
that extend upward from the underside surface 98a and extend along
opposite sides of the rear end 90b of the main body 90. The support
bracket 98 has a front portion 98d and a rear portion 98e. The
support bracket 98 is formed with two parallel elongated slots 98s
that extend from proximate the front portion 98d rearward toward
the rear portion 98e. The slots 98s are angularly offset from the
center line C.sub.L of the vehicle 10. Specifically, the slots 98s
extend in directions that are parallel (or in alignment with) a
lengthwise direction of the main body 90 of the push arm assembly
70. The support bracket 98 also includes two apertures 98f.
[0114] The mechanical fasteners F.sub.1 inserted through the slots
98s and the apertures 98f rigidly attach the support bracket 98 to
the frame 22 and the off-center impact reinforcement structure 12.
Specifically, the mechanical fasteners F.sub.1 in the slots 98s
thread into a nut or threaded aperture formed in the main body 90
of the push arm assembly 70. The mechanical fasteners F.sub.1
inserted through the apertures 98f are threaded into nuts or
threaded apertures of the first cross-member 34 and/or threaded
apertures in a forward portion of the first structure 72. By
removing the mechanical fasteners F.sub.1, the support bracket 98
is held in place covering the pivot bolt 54 of the first suspension
structure 48, the energy absorbing structure 94 and the pivot
bracket 96 of the push arm assembly 70, as shown in FIGS. 9, 11,
15, and 23. However, with the support bracket 98 removed from the
off-center impact reinforcement structure 12, the pivot bolt 54 of
the first suspension structure 48, the energy absorbing structure
94 and the pivot bracket 96 of the push arm assembly 70 are
exposed, as shown in FIGS. 20, 24 and 25.
[0115] As is described in greater detail below, in response to an
off-center impact event the push arm assembly 70 can undergo
limited rearward movement that is initially guided by movement of
the mechanical fasteners F.sub.1 which are configured to slide
along the length of the elongated slots 98s. In other words, impact
force pushing on the push arm assembly 70 causes the main body 90
to move relative to the support bracket 98 during initial stages of
an impact event. The slots 98s are specifically configured to allow
movement of the main body 90 with respect to the support bracket
98, thereby absorbing impact energy, and causing deformation of the
energy absorbing structure 94, as described in greater detail
below. Further, since the connection between the main body 90 and
the support bracket 98 allows for limited movement due to the slots
98s, the attachment of the support bracket 98 to the first
cross-member 34 has greater strength than the connection between
the support bracket 98 and the push arm assembly 70.
[0116] As shown in FIGS. 10, 12-14, 16-17 and 60, the attachment
bracket 100 extends upward from a mid-section 90e of main body 90
of the push arm assembly 70 to the first side member 30 at a
location forward of the intersection 66 of the first side member 30
and the first cross-member 34. In other words, the attachment
bracket 100 extends downward from the first side member 30 to the
upper surface of the main body 90 of the push arm assembly 70.
[0117] Upper ends of the attachment bracket 100 can include hooks
that are inserted into apertures of the first side member 30 during
installation. Mechanical fasteners are then installed through
separate apertures for fixedly attaching the attachment bracket 100
to the first side member 30.
[0118] The attachment bracket 100 is also fixedly attached to the
upper surface of the main body 90 of the push arm assembly 70.
Consequently, the push arm assembly 70 is supported such that the
push arm assembly 70 is located below the first side member 30. The
attachment bracket 100 does not need to be a structural element of
the off-center impact reinforcement structure 12. Rather, the
attachment bracket 100 can be made of a thin sheet metal material
that supports the main body 90 of the push arm assembly 70 in a
non-impacted state. However, in response to an impact event, the
attachment bracket 100 releases the push arm assembly 70 in a
manner described in greater detail below.
[0119] A description of the first structure 72 (a first diagonal
structure) is now provided with specific reference to FIGS. 9, 15,
19, 24 and 37-38. The first structure 72 extends from the first
cross-member 34 rearward to a mid-portion 36a of the second
cross-member located forward of the second structure 76. More
specifically, the first structure 72 is coupled to the first
cross-member 34 at a location that is rearward of and adjacent to,
but inboard relative to the intersection 66 of the first
cross-member 34 and the first side member 30. The first structure
72 (also referred to as a diagonal structure) is neither parallel
to nor perpendicular to either the first cross-member 34 or the
first side member 30. Rather, the first structure 72 extends at an
oblique angle rearward from the first cross-member 34 to the
mid-portion 36a of the second cross-member 36.
[0120] The first structure 72 basically includes a hollow beam 112,
and a bracket 114. The hollow beam 112 has a front end 112a with an
end plate 116 shaped to conform to an adjacent surface of the first
cross-member 34. However, the end plate 116 is spaced apart from
the adjacent surface of the first cross-member 34 defining a gap
G.sub.2 therebetween, as shown in FIG. 24. The hollow beam 112 also
has a rear end 112b that is described in greater detail below along
with the second structure 76 and the gap maintaining structure
78.
[0121] As shown in FIG. 38, associated with the first structure 72
are two secondary members, the secondary reinforcement cross-member
74 and a bracket 120.
[0122] As shown in FIGS. 9, 11, 34, 35, 37 and 38, the bracket 120
extends from the first cross-member 30 to the second cross-member
32. The bracket 120 is positioned adjacent to the second side
member 32. The secondary reinforcement cross-member 74 extends from
the hollow beam 112 to the bracket 120. The secondary reinforcement
cross-member 74 is an optional feature that is parallel to the
first cross-member 34. The secondary reinforcement cross-member 74
is shaped to extend upward to a level that is higher above the
ground than both the first cross-member 34 and the second
cross-member 36, as shown in FIG. 34. The secondary reinforcement
cross-member 74 is positioned such that it extends immediately in
front of a power plant M of the vehicle 10. The power plant M can
be an internal combustion engine, such as a diesel or gasoline
powered engine, a hybrid engine or an electric motor, depending
upon the vehicle design. The secondary reinforcement cross-member
74 extends upward from bracket 120 and the hollow beam 112 such
that a central portion of the secondary reinforcement cross-member
74 extends in front of the power plant M. During an impact event,
the mass of the power plant M, due to the laws of physics, will
continue with forward momentum while the vehicle 10 impacts the
barrier B and forward movement of the vehicle 10 is reduced or
stopped. The secondary reinforcement cross-member 74 can be
contacted by the power plant M during the impact event, thereby
limiting forward movement of the power plant M.
[0123] A description of the effects of an off-center impact event
(a small overlap test) on the push arm assembly 70 of the
off-center impact reinforcement structure 12 is now provided with
specific reference to FIGS. 4-6 and 26-33. As described above, in
an off-center impact event, for instance, during a small overlap
test, the vehicle 10 is provided with velocity and aimed to impact
the fixed barrier B, as shown in FIG. 4. In FIG. 5 as the vehicle
10 impacts the fixed barrier B and the vehicle 10 absorbs impact
energy. The absorption of impact energy includes distribution of
the impact energy to various portions of the frame 22 via the
features of the off-center impact reinforcement structure 12. As
the impact event progress, as shown in FIGS. 5 and 6, the
off-center impact reinforcement structure 12 absorbs a portion of
the impact energy and distributes the impact energy in a manner
described below.
[0124] As shown in FIG. 26 the small overlap test is designed such
that the vehicle 10 makes contact with the barrier B in the area of
the front end plate 92 of the push arm assembly 70. Initially,
impact energy is directed diagonally (rearward and laterally) from
the front end plate 92 in the direction of the gap maintaining
structure 78 (a cross-car direction) as indicated by the large
arrow superimposed over portions of the off-center impact
reinforcement structure 12 in FIG. 26. The impact energy of the
small overlap test is such that the front end plate 92 transmits
impact force through the main body 90 causing the main body 90 to
move rearward resulting in the impact energy being directed
rearward and laterally, as shown in FIG. 27. Several impact
absorbing changes occur as the main body 90 moves rearward relative
to the frame 22, as explained further below. As shown in FIG. 27,
the main body 90 begins to rotate about the intersection 66 of the
first side member 30 and the first cross-member 34. As also shown
in FIG. 27, the impact force is largely directed in a vehicle
lateral direction, as indicated by the large arrow superimposed
over the push arm assembly 70 in FIG. 27. The rotation of the main
body 90 causes at least a portion of the impact energy from the
small overlap test to push the vehicle 10 laterally away from the
barrier B. Further, as shown in FIG. 28, rotation of the main body
90 causes the main body 90 and the barrier B to press against a
front wheel T of the vehicle 10, causing the front wheel T to
contact the stop structure 80, as is described in greater detail
below. As shown in FIG. 28, once the front wheel T contacts the
stop structure 80, impacting force is directed rearward and
laterally (another cross-car direction) as indicated by the large
arrow superimposed over the front wheel T. Further, as shown in
FIG. 28, in the final stages of the impact event, the push arm
assembly 70, and in particular, the main body 90, has pivoted such
that the main body 90 is parallel to or in alignment with the first
cross-member 34.
[0125] As shown in FIG. 29-33, as the main body 90 is pushed
rearward by contact with the barrier B, the main body 90 slides
rearward relative to the support bracket 98, as shown in FIG. 33.
In FIGS. 29-32 the support bracket 98 is removed to show movement
of the main body 90 and compression of the energy absorbing
structure 94. During the small overlap test, the support bracket 98
is installed. The support bracket 98 is shown in phantom in FIG.
33. In the initial stages of the impact event, impact force is such
that the fasteners F.sub.1 that attached the main body 90 to the
support bracket 98, slide along the slots 98e. The slots 98e are
oriented and dimension to direct the rearward movement of the main
body 90 in a direction toward the intersection 66 of the first side
member 30 and the first cross-member 34. Hence, in the initial
moments of the impact event (the small overlap test), the main body
90 slides rearward toward the intersection 66 as directed by the
orientation of the slots 98e.
[0126] As the main body 90 is urged to move toward the intersection
66, the gap G.sub.1 between rear end 90b of the main body and first
cross-member 34 at the intersection 66 begins to close, as shown in
FIG. 30-33. As a result of the closing of the gap G.sub.1, the
pivot bracket 96 contacts the first cross-member 34 inboard of the
intersection 66 providing the main body 90 with a pivot point about
which the front end plate 92 of the main body 90 begins to rotate
rearward and laterally outboard away from the first side member 30.
Once the main body 90 begins to pivot about the pivot bracket 96,
the energy absorbing structure 94 absorbs a portion of the impact
energy and is deformed, as shown in FIGS. 30-33. The cup-shape of
the first and second cup-shaped members 104 and 106 is such that
contact with the bolt 54 securing the lower control arm 52 to the
first side member 30 is avoided, thereby maintaining attachment
between the first side member 30 and the lower control arm 52. In
other words, the shape and configuration of the elements that
define the energy absorbing structure 94 protect the bolt 54 and
prevent the lower control arm 52 from being released from the first
side member 30 during the impact event. As shown in the sequence
depicted in FIGS. 30-33, the energy absorbing structure 94 is
configured such that in response to the impact event of the small
overlap test (the off-center impact event) against the front end
plate 92 of the push arm assembly 70, the push arm assembly 70 via
the main body 90 imparts impact force to the energy absorbing
structure 94 pushing the energy absorbing structure 94 into contact
with the front suspension structure 48 such that the energy
absorbing structure 94 is deformed absorbing impact energy. The
deformation of the energy absorbing structure 94 can take many
forms. For example, the side walls 106a and 106b can deform and
move away from one another (diverging movement) or can deform and
move toward one another (converging movement). It is also possible
for one of the side walls 106a and 106b to move toward the other,
while the other remains unmoved. Further, one or both of the side
walls 106a and 106b can be provided with a notch or score-line (not
shown) that encourages a direction of deformation during the impact
event.
[0127] Further, the pivot bracket 96 is configured and positioned
such that in response to the off-center impact event against the
push arm assembly 70, the main body 90 moves the pivot bracket 96
into contact with the first cross-member 34 and imparts impact
force to the pivot bracket 96 pushing the energy absorbing
structure 94 into contact with the front suspension structure 48.
Further, the push arm assembly 70 pivots about the contact area
between the pivot bracket 96 and the first cross-member 34
providing a pivot point about which the front surface 92a and 92b
of the push arm assembly 70 pivots.
[0128] As is described further below, impact energy is further
transmitted through the first cross-member 34 to the first
structure 72, the second cross-member 36, through the gap
maintaining structure 78 and thereafter to the second structure 76.
Description of the further transmitted impact force follows the
description of the second structure 76, the gap maintaining
structure 78 and the bulkhead structure 80.
[0129] A description of the second structure 76, the gap
maintaining structure 78 and the bulkhead structure 80 is now
provided with specific reference to FIGS. 35-56. The second
structure 76, the gap maintaining structure 78 and the bulkhead
structure 80 are inter-related structures and therefore are
describe together.
[0130] The second structure 76 is another diagonal structure that
extends from the mid-portion 36c of the second cross-member 36 to a
portion of the second side member 32 adjacent to the body
attachment flange 44 and rearward of the second cross-member 36, as
shown in FIGS. 35 and 37. The second structure 76 basically
includes a beam 130 (FIGS. 39, 46, 51 and 52), an end plate 132
(FIGS. 39 and 51), a rear attachment structure 134 (FIGS. 46-50)
and a secondary diagonal structure 136 (FIGS. 35 and 37).
[0131] The gap maintaining structure 78 includes an upper
attachment bracket 140, a first lower attachment bracket 142 and a
second lower attachment bracket 144.
[0132] The bulkhead structure 80 is defined relative to the second
cross-member 34, which includes an upper portion 150 and a lower
portion 152. The bulkhead structure 80 includes a first
reinforcement bracket 154 and a second reinforcement bracket 156
that are installed to a hollow interior of the second cross-section
member 34 between the upper portion 150 and the lower portion 152,
as described below.
[0133] As shown in FIGS. 39, 46, 51 and 52, the beam 130 of the
second structure 76 has a forward end 130a and a rearward end 130b.
An upper wall of the forward end 130a of the beam 130 includes a
first slot 130c and a second slot 130d shown in FIG. 52. The first
and second slots 130c and 130d are aligned with one another and are
configured to receive mechanical fasteners extending from the upper
attachment bracket 140, as is described in greater detail below.
The end plate 132 is fixedly attached to the rearward end 130b of
the beam 130 by, for example, welding techniques. The end plate
132, as shown in FIGS. 39 and 51, has two surfaces, with the
surface 132a extending in a vehicle longitudinal direction parallel
to the center line C.sub.L of the vehicle 10. A description of the
end plate 132 and its relationship to the rear attachment structure
134 is provided below. A description of the secondary diagonal
structure 136 is included after a description of the bulkhead
structure 80, the gap maintaining structure 78 and the rear
attachment structure 134.
[0134] As shown removed from the frame 22 in FIGS. 42 and 44, the
second cross-member 36 includes the upper portion 150 and the lower
portion 152. The upper portion 150 includes a reinforcement 150a
that is welded to outer surfaces of the upper portion 150. The
lower portion 152 has a first upright wall 152a, a horizontal wall
152b and a second upright wall 152c, as shown in FIG. 44. The first
and second upright walls 152a and 152c are parallel to one another
with a recessed area being defined between them above the
horizontal wall 152b, as shown in FIG. 44.
[0135] The first reinforcement bracket 154 has a first upright
portion 154a, a first horizontal portion 154b and a second upright
portion 154c that together define the plurality of surface sections
perpendicular to the first upright wall 152a and the second upright
wall 152c. The second reinforcement bracket 156 defines a third
upright portion 156a and a second horizontal portion 156b that
installed within the recess or hollow area of the lower portion 152
of the second cross-member 36. The third upright portion 156a and
the second horizontal portion 156b both define additional surface
sections perpendicular to the first upright wall 152a and the
second upright wall 152c of the second cross-member 36.
[0136] The first reinforcement bracket 154 of the bulkhead
structure 80 is welded within the recessed area of the lower
portion 150 via welds W. The second reinforcement bracket 156 is
welded to the lower portion 152 with the recessed area and is
further welded to an upper surface of the first reinforcement
bracket 154. After the first and second reinforcement brackets 154
and 156 are welded in place, the upper portion 150 is welded to the
lower portion 152 thereby completing the second cross-member 36. In
the completed second cross-member 36, the bulkhead structure 80 is
installed within a hollow interior of the second cross-member 34
between the upper portion 150 and the lower portion 152.
[0137] Thereafter, the second cross-member 36 can be installed to
the first and second side member 30 and 32 and held in place by
fasteners (not shown). As discussed further below, the bulkhead
structure 80 reinforces the second cross-member 36 such that in
response to an impact event, the second cross-member 36 resists
being crushed or deforming. Impact forces on one side of second
cross-member 36 in FIG. 44, will be first transmitted through
reinforcement brackets 154 and 156 and then transmitted to the
other side of second cross-member 36. Reinforcement brackets 154
and 156 transmit a column load from one side of second cross-member
36 to the other side of second cross-member 36 and improve the
strength of second cross-member 36.
[0138] As shown in FIG. 36, the upper attachment bracket 140 of the
gap maintaining structure 78 is welded to an upper surface 36b of
the second cross-member 36. As is discussed further below, the
welds W that fix the upper attachment bracket 140 to the second
cross-member 36 can be tuned to have a predetermined level of
strength. Specifically, during normal operating conditions of the
vehicle 10, the welds W fixing the upper attachment bracket 140 to
the second cross-member 36 have more than enough strength to retain
the upper attachment bracket 140 in position. The upper attachment
bracket 140 extends rearward away from the second cross-member 36.
However, during an impact event, where impact forces acting on the
first structure 72 are transmitted to the second cross-member 36
(as described further below) the welds W between the upper
attachment bracket 140 to the second cross-member 36 can be tuned
to release the upper attachment bracket 140 from the second
cross-member 36. One method of tuning the strength of welds W is to
alter the overall length of one or more of the welds W.
[0139] As shown in FIG. 36, the upper attachment bracket 140 of the
gap maintaining structure 78 includes recessed areas 140a and 140b.
The recessed area 140a is dimensioned and configured to receive the
forward end 130a of the beam 130 of the second structure 76 and the
recessed area 140b is dimensioned and configured to receive a
forward end of the secondary diagonal structure 136, as described
further below. It should be understood from the drawings that FIG.
36 shows an upper surface of the upper attachment bracket 140, and
that the recessed areas 140a and 140b define concaved areas of an
underside surface of the upper attachment bracket 140 that is not
visible in FIG. 36. Rather, FIG. 36 shows convex areas
corresponding to the recessed areas 140a and 140b.
[0140] FIG. 53 shows a lower surface of the upper attachment
bracket 140 extending rearward from the second cross-member 36. The
secondary diagonal structure 136 is installed to the upper
attachment bracket 140 within the recessed area 140b. The recessed
area 140a is visible in FIG. 52. Fasteners F.sub.2 are installed to
threaded the upper attachment bracket 140 in order to receive the
forward end 130a of the beam 130 of the second structure 76.
[0141] The welds W that fix the upper attachment bracket 140 to the
second cross-member 36 are provided with a first shear strength.
The mechanical fasteners F.sub.2 are provided with a second shear
strength stronger than the first shear strength such that in
response to the off-center impact event, the welds W release the
upper attachment bracket 140 from the second cross-member 36 with
the upper attachment bracket 140 remaining above the second
cross-member 36 supporting the second structure 76 thereby limiting
vertical movement of the second structure 76 relative to the second
cross-member 36.
[0142] The first lower attachment bracket 142 of the gap
maintaining structure 78 is shown removed from the vehicle 10 in
FIGS. 40 and 41. The first lower attachment bracket 142 includes a
U-shaped portion 142a, a first angled portion 142b and a second
angled portion 142c. As shown in FIG. 40, the U-shaped portion
142a, the first angled portion 142b and the second angled portion
142c are welded together. The U-shaped portion 142a defines a
recessed area that receives the rear end 112b of the hollow beam
112, as shown in FIGS. 35 and 36.
[0143] The second lower attachment bracket 144 is attached to the
mid portion 36a of the second cross-member 36 via mechanical
fasteners (not shown) or welding techniques. The second lower
attachment bracket 144 has side walls 144a and 144b that contact
opposite lateral sides of the hollow beam 112 of the first
structure 72, as shown in FIGS. 37 and 38.
[0144] With the off-center impact reinforcement structure 12
installed to the frame 22 in the non-impacted state, there are
several gaps maintained between the various elements of the first
structure 72, the second cross-member 36 and the second structure
74. Specifically, as shown in FIG. 36 (in phantom) a gap G.sub.3 is
defined between the rear end 112b and an adjacent front surface of
the second cross-member 36. Further, a gap G.sub.4 is defined
between a rear surface of the second cross-member 36 and a forward
end 130a of the beam 130 of the second structure 76. Also, a gap
G.sub.5 is defined between a side surface of the beam 130 of the
second structure 76 and a front end of the secondary diagonal
structure 136.
[0145] The gaps G.sub.3, G.sub.4 and G.sub.5 are maintained during
normal operation of the vehicle 10 in the non-impacted state by the
gap maintaining structure 78. Specifically, the rear end 112b of
the hollow beam 112 is restricted against lateral movement being
confined between the side walls 144a and 144b of the second lower
attachment bracket 144. Further, movement of the rear end 112b of
the hollow beam 112 is also limited by engagement with the recessed
area defined by the U-shaped portion 142a of the first lower
attachment bracket 142. Thus, the gap G.sub.3 is maintained between
the second cross-member 36 and the rear end 112b of the hollow beam
112.
[0146] It should be understood from the drawings and the
description herein that the rear end 112b of the hollow beam 112
can be welded to the second lower attachment bracket 144 or can be
fixed thereto via mechanical fasteners. Alternatively, the hollow
beam 112 can merely be retained in place by contact with the second
lower attachment bracket and the first lower attachment bracket
142. In the depicted embodiment, the rear end 112b of the hollow
beam 112 is not fixed to the first lower attachment bracket 142,
but rather is configured to move relative to the first lower
attachment bracket 142 during an impact event, as is described
further below.
[0147] The gap G.sub.4 is maintained via a connection between the
upper attachment bracket 140 and the forward end 130a of the beam
130. Specifically, the slots 130c and 130d are fitted to the
fasteners F.sub.2 of the upper attachment bracket 140, as shown in
phantom in FIG. 36. The fasteners F.sub.2 of the upper attachment
bracket 140 are also shown in FIGS. 39 and 53. The slots 130c and
130d are elongated, as shown in FIGS. 36 and 52. Therefore, once
the beam 130 is slid on to the fasteners F.sub.2, and moved to the
position shown in FIG. 16, the beam 130 is able to undergo sliding
movement relative to the upper attachment bracket 140. However,
contact between the fasteners F.sub.2, and the beam 130 prevents or
limits vertical movement of the beam 130 during normal operation of
the vehicle 10. As shown in FIGS. 51 and 54, the beam 130
additionally includes a large slot 130e and an aperture 130f. As
shown in FIG. 54, once the beam 130 is slid on to the fasteners
F.sub.2, the fasteners F.sub.2 can be accessed by tools via the
slot 130e and the aperture 130f and tightened to secure the beam
130 to the upper attachment bracket 140.
[0148] It should be understood from the drawings and the
description herein, that each of the upper attachment bracket 140,
the first lower attachment bracket 142 and the second lower
attachment bracket 144 includes a recess or recessed area that
retains a beam member of one of the first structure 72 and the
second structure 76 in the non-impacted state. Further, the recess
or recessed area of each of the upper attachment bracket 140, the
first lower attachment bracket 142 and the second lower attachment
bracket 144 guides movement of the corresponding beam member of one
of the first structure 72 and the second structure 76 in response
to an impact event, as is described in further below.
[0149] The secondary diagonal structure 136 is a hollow beam
member, as shown in FIGS. 35 and 55. The forward end of the
secondary diagonal structure 136 is attached to the upper
attachment bracket 140 via two of the fasteners F.sub.2. The
rearward end of the secondary diagonal structure 136 includes and
end plate 136a welded in place to the secondary diagonal structure
136. The rearward end of the secondary diagonal structure 136 is
coupled to the first side member 30 in a manner consistent with the
attachment of the beam 130 to the second side member 32.
Description of the attachment structure fixing of the rearward end
of the secondary diagonal structure 136 to the first side member 30
is provided below with a description of the rear attachment
structure 134.
[0150] The rear attachment structure 134 includes structural
members that couple the rearward end 130b of the beam 130 to the
second side member 32. Specifically, the rear attachment structure
134 includes a first bracket 160, a second bracket 162 and a
stopper bracket 164. The secondary diagonal structure 136 is
coupled to the first side member 30 using structures that are
identical, except that they are mirror images thereof. Therefore,
the description below of the coupling between the beam 130 to the
second side member 32 (FIGS. 46-50) applies equally to the coupling
of the secondary diagonal structure 136 to the first side member 30
(FIGS. 55 and 56). More specifically, the shape and installation of
the first bracket 160, the second bracket 162 and the stopper
bracket 164 to the second side member 32 also applies to
installation to the first side member 30, except that the coupling
to the first side member 30 is applied to the secondary diagonal
structure 136.
[0151] As shown in FIGS. 35 and 46-50, the first bracket 160 is
welded to an underside surface of the second side member 32. The
second bracket 162 is welded to an inboard side surface of the
second side member 32, with the stopper bracket 164 welded within a
recess defined within the second bracket 162. As shown in FIGS. 46
and 47 (and FIG. 55 with respect to the secondary diagonal
structure 136), the rearward end 130b of the beam 130 extends into
a pocket defined between the first bracket 160 and the second
bracket 162. Further, the beam 130 can be fixed to the second
bracket by mechanical fasteners (not shown) or by welds (not shown)
that are tuned to release the beam 130 in response to an impact
event. Hence, the beam 130 is prevented from lateral, vertical and
horizontal movement in the non-impacted state. A gap G.sub.6 is
maintained between the surface 132a of the end plate 132 of the
beam 130 and the stopper bracket 164 in the non-impacted state.
However, as described below, in response to an impact event, the
gap G.sub.6 can be closed bringing the surface 132a of end plate
132 of the beam 130 into contact with the stopper bracket 164.
[0152] As shown in FIG. 35, when fully installed in the
non-impacted state, the beam 130 of the second structure 76 defines
an angle .alpha.6 relative to the second cross-member 36 that is
between 35 and 60 degrees. In the depicted embodiment, the an angle
.alpha.6 is between 40 and 50 degrees, and is preferably
approximately 45 degrees.
[0153] A description is now provided of the stop structure 82 with
specific reference to FIGS. 35 and 57-59. As shown in FIGS. 35 and
57, the stop structure 82 is installed to the first side member 30
adjacent to (but forward of) the third cross-member 38. The stop
structure 82 is also rigidly fixed to the body attachment flange
44.
[0154] As shown in FIG. 58, the stop structure 82 (a tire catcher)
basically includes a lower plate 170, an upper plate 172, a
reinforcement plate 174 (a mid-plate) and an outer plate 176 (a
main plate). As shown in FIG. 58, the lower plate 170, the upper
plate 172 and the reinforcement plate 174 are all horizontally
oriented and are spaced apart from one another. The lower plate 170
defines a bottom of the stop structure 82 and the upper plate 172
defines a top of the stop structure 82. The reinforcement plate 174
is located between the upper plate 172 and the lower plate 170.
[0155] The outer plate 176 has first section 176a attached to the
first side member 30, a second section 176b defining a stop surface
and a third section 176c that wraps around the lower plate 170, the
upper plate 172 and the reinforcement plate 174 forming a box-like
structure, with the reinforcement plate 174 being concealed by the
outer plate 176 or enclosed within the outer plate 176. The outer
plate 176 is vertically oriented and the lower plate 170, the upper
plate 172 and the reinforcement plate 174 are generally
horizontally oriented in the non-impacted state. The plates of the
stop structure 82 are welded to one another and welded to the first
side member 30.
[0156] As shown in FIG. 35, at least the third section 176c of the
outer plate 176 is rigidly attached to the body attachment flange
44 (a cabin attachment flange) via, for example, welding
techniques.
[0157] As shown in FIG. 35, the second section 176b (the stop
surface) is a forward facing surface. The second section 176b (the
stop surface) of the stop structure 82 defines an angle as relative
to a vehicle longitudinal direction that is between 110 and 130
degrees. In the depicted embodiment, the angle .alpha..sub.5 is
approximately 120 degrees. The angle as is selected such that in
response to an off-center impact event that directs an impacting
force to a front surface area of the front wheel T, the front wheel
T pivots relative to the wheel support structure 48 and moves a
rear surface area of the front wheel T into contact with the second
section 176 (the stop surface) with the stop structure 82 absorbing
at least a portion of the impacting force restricting further
pivoting movement of the front wheel T, as shown in FIG. 59.
[0158] A further description of the effects of the off-center
impact event (the small overlap test) on the push arm assembly 70
of the off-center impact reinforcement structure 12 is now provided
with reference to all drawings.
[0159] As the push arm assembly 70 is being impacted, the gap
G.sub.1 between the main body 90 of the push arm assembly 70 closes
causing the pivot bracket 96 to move into contact with the first
cross-member 32, and collapsing the energy absorbing structure 94.
The first cross-member 32 can undergo some deformation thereby
closing the gap G.sub.2 between the first cross-member 32 and
hollow beam 112 of the first structure 72. Impact forces
transmitted through the hollow beam 112 of the first structure 72
cause the end plate 116 at the rear end 112b of the hollow beam 112
to move toward the second cross-member 36, thereby closing the gap
G.sub.3.
[0160] The hollow beam 112 is guided to move toward the second
cross-member 36 during the impact event due to the recessed areas
of the first and second lower attachment brackets 142 and 144.
Specifically, the first and second lower attachment brackets 142
and 144 being rigidly fixed to the second cross-member 36 and
having the U-shaped portion 142a and the side walls 144a and 144b,
limit or prevent lateral in an inboard or outboard direction, and
further limit or prevent vertical movement of the hollow beam 112
relative to the second cross-member 36. Therefore, impact forces
close the gap G.sub.3 thereby directing the impact force against
the second cross-member 36.
[0161] Once the gap G.sub.3 closes, the impact force is thereafter
transmitted from the hollow beam 112 to the second cross-member 36.
Within the second cross-member 36, the bulkhead structure 80 limits
and/or prevents the second cross-member 36 from collapsing,
although the second cross-member 36 can undergo limited overall
bending deformation. Consequently, the second cross-member 36 bends
such that force is transmitted through the second cross-member 36
via the upper attachment bracket 140.
[0162] Rearward movement of the second cross-member 36 and the
upper attachment bracket 140 subsequently can do two things. First,
the linearly aligned first and second slots 130c and 130d allow the
beam 130 to slide relative to the fasteners F.sub.2 that are fixed
to the upper attachment bracket 140, thereby closing the gap
G.sub.a. Second, the welds W fixing the upper attachment bracket
140 to the second cross-member 36 can release the upper attachment
bracket 140 from fixed attachment to the second cross-member 36.
Since the upper attachment bracket 140 remains above the second
cross-member 36 even after release by the welds W, the upper
attachment bracket 140 can undergo some lateral movement relative
to the second cross-member 36. However, the upper attachment
bracket 140 prevents downward movement of the beam 130 since the
fasteners F.sub.2 remain fixed to the upper attachment bracket 140
and to the beam 130. Further, the gap G.sub.5 defined between the
beam 130 of the second structure 76 and the front end of the
secondary diagonal structure 136 can also close.
[0163] Next, impact forces are transferred from the second
cross-member 36 to the beam 130 and optionally to the secondary
diagonal structure 136. Each of the beam 130 and the secondary
diagonal structure 136 can undergo limited rearward movement due to
the gap G.sub.6 between the surface 132a of the end plate 132 of
the beam 130 and the stopper bracket 164. Specifically, sliding
movement of the beam 130 relative to the first and second brackets
160 and 162 causes the gap G.sub.6 to close such that impact energy
is transmitted from the beam 130 through the stopper bracket 164
and to the second side member 32. Similarly, the secondary diagonal
structure 136 can transmit some of the impact energy to the first
side member 30.
[0164] Further, during the impact event as impact forces from the
stationary barrier B act on the push arm assembly 70, the impact
forces also act on the front wheel T causing deformation of at
least one of the first side member 30, the front suspension
structure 48 and/or the lower control arm 52. The force acting on
the front wheel T urge the front wheel T into contact with the stop
structure 82.
[0165] The various movements of the components of the off-center
impact reinforcement structure 12 have the effect of distributing
the impact forces of the impact event throughout the frame 22 of
the vehicle 10. The off-center impact reinforcement structure 12
also causes the vehicle 10 to move laterally away from the fixed
barrier B during the impact event.
[0166] The various features of the vehicle 10, other than the
off-center impact reinforcement structure 12 are conventional
components that are well known in the art. Since such components
are well known in the art, these structures will not be discussed
or illustrated in detail herein. Rather, it will be apparent to
those skilled in the art from this disclosure that the components
can be any type of structure and/or programming that can be used to
carry out the present invention.
General Interpretation of Terms
[0167] In understanding the scope of the present invention, the
term "comprising" and its derivatives, as used herein, are intended
to be open ended terms that specify the presence of the stated
features, elements, components, groups, integers, and/or steps, but
do not exclude the presence of other unstated features, elements,
components, groups, integers and/or steps. The foregoing also
applies to words having similar meanings such as the terms,
"including", "having" and their derivatives. Also, the terms
"part," "section," "portion," "member" or "element" when used in
the singular can have the dual meaning of a single part or a
plurality of parts. Also as used herein to describe the above
embodiment(s), the following directional terms "forward",
"rearward", "above", "downward", "vertical", "horizontal", "below"
and "transverse" as well as any other similar directional terms
refer to those directions of a vehicle equipped with the vehicle
structure. Accordingly, these terms, as utilized to describe the
present invention should be interpreted relative to a vehicle
equipped with the vehicle structure.
[0168] The term "configured" as used herein to describe a
component, section or part of a device includes structure that is
constructed to carry out the desired function.
[0169] The terms of degree such as "substantially", "about" and
"approximately" as used herein mean a reasonable amount of
deviation of the modified term such that the end result is not
significantly changed.
[0170] While only selected embodiments have been chosen to
illustrate the present invention, it will be apparent to those
skilled in the art from this disclosure that various changes and
modifications can be made herein without departing from the scope
of the invention as defined in the appended claims. For example,
the size, shape, location or orientation of the various components
can be changed as needed and/or desired. Components that are shown
directly connected or contacting each other can have intermediate
structures disposed between them. The functions of one element can
be performed by two, and vice versa. The structures and functions
of one embodiment can be adopted in another embodiment. It is not
necessary for all advantages to be present in a particular
embodiment at the same time. Every feature which is unique from the
prior art, alone or in combination with other features, also should
be considered a separate description of further inventions by the
applicant, including the structural and/or functional concepts
embodied by such feature(s). Thus, the foregoing descriptions of
the embodiments according to the present invention are provided for
illustration only, and not for the purpose of limiting the
invention as defined by the appended claims and their
equivalents.
* * * * *