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Патент USA US3052443

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Sept. 4, 1962
A. E. ROLLER
3,052,435
VIBRATION DAMPING AND SHOCK ABSORBING
RESILIENT ENGINE MQUNTING
Filed Dec. 19, 1960
INVEN TOR.
rice
3,052,435!
Patented Sept. 4, 1962
2
shank portion and is externally threaded as indicated at
46. The lower end of the bolt 40 is provided with a
hexagonal head 48 for the purpose of turning the bolt in
assembly and in adjustment of the mounting device. The
large diameter and shank portions of the bolt de?ne an
3,052,435
VIBRATION DAMPING AND SHOCK ABSORB-ING
RESHJENT ENGINE MOUNTING
Albert E. Roller, Birmingham, Mich., assignor to General
Motors Corporation, Detroit, Mich., a corporation of
Delaware
annular shoulder 59 which is engaged by one end of a
spool assembly 52 mounted on the reduced diameter
Filed Dec. 19, 1966, Ser. No. 76,684
12 Claims. (Cl. 248-8)
shank portion of the bolt. This spool assembly comprises
two end ?ange de?ning disk or washer members 54 and
This invention relates to a resilient mounting device 10 58 ‘which are maintained in spaced parallel relation to
constituting a vibration damping and shock absorbing con
each other and to the oppositely disposed ends of the
nection between a supporting and supported structure
bracket de?ned recesses 18 and 24 by an intermediate
and having particular application in supporting an internal
spacer sleeve 56. These spool de?ning elements are
combustion engine within the frame of a motor vehicle.
clamped together on the bolt by a nut 60 which is thread
The invention contemplates an improved and relatively
ably tightened and suitably locked on the upper bolt
simple resilient engine mounting which is of economical
easily assembled construction, which is adjustable to pro
portion 46.
In assembly, two resilient rebound limiting grommets or
vide desired variable rate rebound characteristics obtain
bushings 62 and 64 are mounted on the spacer sleeve of
ing optimum vibration damping and mounting life and
the spool assembly within the bracket de?ned recesses 18
which is particularly adapted to isolate and damp the 20 and 24. These rebound grommets are interchangeable
vibration and torsional reactions of the engine from trans
mission to the vehicle frame and body while at the same
and formed of rubber or like resilient material. Each
grommet is beveled inwardly from its opposite ends to
an inner surface 66 of reduced axial dimension. These
time isolating the engine housing from road shocks and
from resultant twisting of the vehicle frame thereby im
reduced inner grommet surfaces and portions frictionally
proving the riding qualities of the motor vehicle and con 25 embrace and resiliently snub the spacer sleeve. The outer
tributing to passenger comfort by reducing the amount of
surfaces 63 of the grommets are convex longitudinally
engine vibration and road shock transmitted through the
thereof. To provide the mounting device with desired
vehicle frame and body.
directional stability and lateral rebound characteristics,
The foregoing and other objects, advantages and fea
the convex outer surface of the lower grommet 64 fric
tures of the invention will be apparent from the follow 30 tionally and resiliently engages the inner surface of the
ing description, having reference to the single FIGURE of
recess de?ning sleeve 22 at 68’. In the illustrative em
the accompanying drawing showing an engine mounting
bodiment, the recess de?ning side wall of the upper
device illustrative of the invention in transverse section.
bracket boss 16 spacedly embraces the upper grommet 62
In the drawing, the frame of an internal combustion
and is resilient engageable thereby only under conditions
engine is partially shown and indicated by the reference
of extreme lateral movement between the engine and
numeral 8. An upstanding ?ange 12 of an engine sup
porting bracket member 10 is secured by bolts 14 to the
side face of the engine frame member. The laterally ex
frame. The relative axial dimensions of the spacer sleeve
and of the rebound limiting grommets provide static as
sembled clearances 70 and 72 between the recess de?ning
tending base portion of this bracket member is stamped to
bottom
wall 19 and the upper and lower grommets 62 and
provide a boss 16 de?ning a cylindrical upwardly open 110 64, respectively. These clearances are preferably equal
ing recess or depression 18 having a bottom wall 19. The
ized by threadable adjustment of the spool carrying bolt
wall 19 is perforated to de?ne an opening 20 extending
relative to the frame member to permit limited substan
centrally therethrough. A cylindrical sleeve 22 is welded
to and cooperates with the bottom wall 19 to de?ne a
second downwardly facing cylindrical recess 24 concentri
cally aligned with the opening 20. The sleeve member
tially free vertical de?ection of the coil spring 26 in either
45 direction before the bracket bottom wall 19 engages either
grommet and compressive rebounding thereof occurs.
Such clearance equalizing adjustment is maintained by a
lock nut 74 threadably tightened into locking engagement
with a lock strip 39. As shown in broken lines, the lock
and the boss 16 are outwardly embraced by a helical
spring 26 which is compressively interposed between the
engine supporting bracket 16 and a vehicle frame member
28. This spring supports the engine weight applied there
to and normally absorbs or damps all of the engine in
duced vibrations and torque reactions occurring within
the normal range of engine operating speed. The upper
end of the spring 26 engages a spring seating washer 30
which in turn engages the base portion of the bracket
member 16 outwardly of the boss 16. A resiliently
backed washer member 32 is interposed between the lower
end of the spring 26 and the lower bottom wall of the
frame member and embraces an upwardly projecting cylin
drical or frusto-conical boss 34 stamped therein.
The upper wall 35 of the frame boss 34 has a central
tapped opening 36 therethrough and is reinforced in as
sembly by a nut 38 nonrotatably secured to its underside
by welding a locking strip 39. A bolt or stud 40 of
stepped diameter has a large diameter lower portion 42
which is screw threaded in the coextensive threads of the
nut 38 and of the opening 36. An intermediate reduced
diameter and unthreaded shank portion of the bolt extends
upwardly through the opening 20 in the upper bracket
member 10. The end of the bolt 40 projecting above the
bracket 10 is of substantially the same diameter as the
50 strip is provided with at least one tab which is subse
quently bent into locking contact with one of the flat side
faces of the nut 74.
The engine supporting spring 26 is preferably selected
to provide a low de?ection rate characteristic having a
55
natural frequency occurring between the engine cranking
and idle speeds, that is having a natural frequency which
is not in resonance with the vibration inducing, engine
unbalance secondary forces occurring within a normal
range of engine operating speed. This spring rate selec
60 tion and the clearances 70 and 72 provided between the
bracket bottom wall 19 and the rebound grommets permit
the vibration inducing unbalance forces to be absorbed or
damped by vertical oscillation of the engine mass on the
coil
springs within the grommet de?ned limits and by the
65
resultant and supplemental in-shear, variable rate de?ec
tions of the rebound grommets. Such vibration damping
oscillations occur at twice the engine rotational speed.
From the foregoing description of a preferred illustra
70 tive embodiment, it will be seen that the invention pro
vides an improved resilient mounting of the type de
scribed and that various modi?cations and changes might
3,052,435
3
be made therefrom without departing from the spirit and
scope of the invention as de?ned in the following claims.
I claim:
~
4
assembly in axially ?xed relation on the bolt, and two
resilient grommets frictionally and resiliently embrac
ing said spool assembly sleeve and interposed between
mounting an internal combustion engine in a motor
said washers and said bracket end wall within said
bracket de?ned recesses, one of said grommets periph
vehicle, said engine mounting device comprising a ve
hicle frame member, an engine supporting bracket mem
ber spaced from said frame member, said bracket member
radially inwardly of the cylindrical surface de?ning its
coil spring interposed between said support and bracket
member in spaced embracing relation to said bolt and
from the opposite axial ends thereof to an inner surface
1. A resilient vibration and shock isolating device for
erally engaging the cylindrical surface of its mounting
recess and the other of said grommets being spaced
mounting recess, said grommets being of axial dimensions
de?ning opposed axially aligned cylindrical recesses
separated by a common end Wall having an opening there 10 to provide predetermined clearances between said spool
assembly washers and said bracket member end wall
through centrally of said recesses, said frame member
under static load conditions and said bolt and spool
having a threaded opening substantially in axial align
assembly being axially adjustable by rotation of said
ment with the opening of said bracket member, a bolt
bolt member relative to the threaded opening of said
threadably mounted adjacent one end thereof within
the threaded opening of said frame member and extend 15 frame member to provide said predetermined clearances
between said grommets and said bracket member end
ing through the opening in said bracket member, a
wall, each of said grommets being beveled inwardly
of reduced axial dimension in resilient engagement with
the spool assembly sleeve whereby said one grommet
provides initial lateral variable rate compressive rebound
resonant frequency within the engine cranking and idle
stability to the mount and is subjected to and provides
speeds, a spool assembly mounted on said bolt compris
initial variable rate vibration damping de?ection supple
ing two end washers and an intermediate spacer sleeve,
menting the vibration damping de?ection of said spring
means for maintaining said spool assembly in axially
?xed relation on the bolt, and two resilient grommets 25 within the rebound limits established by the static load
clearances provided between said grommets and end
frictionally and resiliently embracing said spool assembly
wall, said other grommet being subjected to and provid
sleeve and interposed between said washers and said
ing additional variable rate lateral rebound stability to
bracket end wall within said bracket de?ned recesses,
supporting the weight of the engine applied thereto,
said spring having a low de?ection rate and a natural
at least one of said grommets peripherally engaging the
cylindrical surface of its mounting recess and said grom
said mount under extreme lateral load conditions, and
both of said grommets being subjected to and providing
variable rate vibration damping de?ection and com~
mets being of axial dimensions to provide predetermined
clearances between said spool assembly washers and
pressive rebound supplementing vibration damping spring‘
said bracket member end wall under static load condi
de?ection beyond the rebound limits established by the
static clearances.
4. A resillient vibration and shock isolating mounting
adjustable by rotation of said bolt member relative to 35
device comprising two support members spaced from
the threaded opening of said frame member to provide
tions, and said bolt and spool assembly being axially
said predetermined clearances between said grommets
and said bracket member end wall,
2. In a vibration isolating mount as set forth in claim
each other and subjected to relative vibration inducing
forces acting therebetween, one of said members having
opposed axially aligned cylindrical recesses separated by
1, each of said grommets being beveled inwardly from 40 a centrally perforated end wall, the other of said mem
bers having a threaded opening therethrough in sub
the opposite axial ends thereof to an inner surface of
reduced axial dimension in resilient ‘frictional engage
ment with said spacer sleeve whereby said recess engag
through the end wall of said one member, a coil spring
ing grommet provides variable rate lateral compressive
interposed between said support members and support
stantially axial alignment with the perforated opening
rebound stability to the mount and is subjected to and 45 ing weight applied thereto, said spring having a natural
resonant frequency below the normal frequency range
provides initial variable rate vibration damping de?ec
of said vibration inducing forces, a spool assembly com
tion supplementing the axial vibration damping de?ec
prising an intermediate portion extending through said
tion of said spring within the rebound limits established
end wall opening between two end ?anges spaced axially
by the static load clearances provided between said
grommets and end wall, both of said grommets being 50 of said opposed recesses and further comprising a support
portion threadably mounted within said threaded open
subjected to and providing variable rate vibration damp
ing for axial adjustment of said spool assembly relative
ing de?ection and compressive rebound supplementing
to said other member, and two resilient grommets fric
vibration damping coil spring de?ection beyond the
tionally and resiliently embracing said intermediate spool
rebound limits established by the static load clearances.
3. A resilient vibration and shock isolating device for 55 portion within said recesses, said grommets being of
axial dimensions providing predetermined clearances be
mounting an internal combustion engine in a motor
tween said spool end ?anges and said recess de?ning
vehicle, said engine mounting device comprising a ve
end wall under static load conditions and said spool
hicle frame member, an engine supporting bracket mem
assembly being adjustable by rotation of its threaded
ber spaced from said frame member, said bracket member
de?ning opposed axially aligned cylindrical recesses 60 support portion relative to the threaded opening of said
other member to provide said predetermined clearances
separated by a common end wall, and having an opening
between said grommets and said end Wall and spool
centrally therethrough of said opposed recesses, said
?anges, One of said grommets peripherally engaging the
frame member having a threaded Opening therethrough
in substantially axial alignment with the opening of said
cylindrical surface de?ning its mounting recess, and the
bracket member, a bolt threadably mounted adjacent 65 other of grommets being spaced radically inwardly of
cylindrical surface de?ning its mounting recess.
one end thereof within the threaded opening of said
frame member and extending through the opening in said
5. ‘In a vibration isolating mount as set forth in claim
bracket member, a coil spring interposed between said
4, each of said grommets being beveled inwardly from
support and bracket member in spaced embracing rela
the opposite axial ends thereof to an inner surface of
tion to said bolt and supporting the weight of the engine 70 reduced axial dimension in resilient engagement with
applied thereto, said spring having a low de?ection rate
the intermediate portion of ‘said spool whereby said one
and a natural resonant frequency within the engine
grommet provides initial lateral variable rate compres
cranking and idle speeds, a spool assembly mounted on
sive rebound stability to the mount and is subjected to
said bolt comprising two end washers and an inter
and provides initial variable rate vibration damping de
mediate spacer sleeve, means for maintaining said spool 75 ?ection supplementing the vibration damping de?ection
3,052,435
of said spring
the rebound limits established by
the static load clearances provided between said grommets
and end wall, said other grommet being subjected to and
providing additional variable rate lateral rebound sta
bility to said mount under extreme lateral load condi
tions, and both of said grommets being subjected to and
providing variable rate vibration damping de?ection and
6
,
least the adjacent axial ends thereof to an inner surface
of reduced axial dimension in resilient engagement with
said intermediate spool portion whereby said one grom
met provides lateral variable rate compressive rebound
stability to the mount and is subjected to and provides
axial variable rate vibration damping de?ection sup
plementing the vibration damping de?ection of said
spring within the rebound limits established by the static
spring ‘de?ection beyond the rebound limits established by
load clearances provided between said grommets and end
the static clearances.
10 wall, both said grommets being subjected to and pro
‘6. A resilient vibration isolating mounting device com
viding variable rate vibration damping de?ection and com
prising two support members spaced ‘from each other,
pression supplementing vibration damping de?ection of
at least one of said members being subjected to vibration
said spring beyond the rebound limits established by the
inducing forces, a coil spring interposed between said
static load clearances.
support members and supporting weight applied thereto,
10. A vibration isolating mount comprising two sup
said spring having a natural resonant frequency below 15 port members spaced from each other, at least one of
the normal vfrequency range of said vibration inducing
said members being subjected to vibration inducing forces,
forces, one of said members having opposed axially
a spring normally supporting the mounted weight applied
aligned cylindrical recesses separated by a cent-rally per
between said members and having a resonant frequency
forated end wall, a spool assembly comprising an inter_
20 below the normal frequency range of said vibration in
compressive rebound supplementing vibration damping
mediate spool portion extending through the perforated
ducing ‘forces, one of said members having an opening
opening in said end wall between two spool end ?anges
therethrough, a spool mounted on the other of said mem~
spaced axially of said opposed recesses and a spool sup
bers comprising an intermediate spool portion extending
port portion adjustably mounted on said other member,
between two end ?anges, said intermediate spool portion
two resilient grommets frictionally and resiliently em~ 25 extending through said opening and spacing said end
bracing said intermediate spool portion within said re
flanges axially on opposite sides of said one member, two
cesses, said grommets being of axial dimensions provid
resilient grommets frictionally and resiliently embracing
ing predetermined clearances between said spool end
said intermediate spool portion and having predetermined
?anges and said recess de?ning end wall under static
clearances with the opposite sides of said one member un
load conditions and said spool support portion. being
.
30 der static load conditions, each of said grommets being
adjusted axially of said other member to provide said
beveled inwardly from at least the adjacent axial ends
predetermined clearances between said grommets and
thereof to an inner surface of reduced axial dimension
said end wall and spool end ?anges, and at least one of
in resilient engagement with the intermediate spool por
said grommet-s peripherally and resiliently engaging the
tion thereby providing initially soft variable rate vi
cylindrical surface de?ning its mounting recess.
35 bration damping de?ection and compression of said grom
7. In a vibration isolating mount as set forth in claim 6,
each of said grommets ‘being beveled inwardly from the
mets supplementing vibration damping de?ection of said
spring beyond the rebound limits established by the stat
opposite axial ends thereof to an inner surface of reduced
ic load clearances ‘between said grommets and said one
‘axial dimension in resilient engagement with said inter
member;
mediate spool portion whereby said one grommet pro 40
11. A resilient vibration and shook isolating device for
vides lateral variable rate compressive rebound stabil
mounting an internal combustion engine in a motor ve
ity to the mount and is subjected to and provides axial
hicle, said engine mounting device comprising a vehicle
variable rate vibration damping de?ection supplementing
frame member, an engine supporting bracket member
the vibration damping de?ection of said spring within the
spaced from said frame member, said frame and bracket
rebound limits established by the static load clearances 45 members having cylindrical bosses thereon extending in
provided between said grommets and end wall, both of
substantial parallel axial alignment to each other and de
said grommets being subjected to and providing variable
?ning opposed parallel end walls, said frame member
rate vibration damping de?ection and compression sup
boss having a threaded opening centrally of the end wall
plementing vibration damping de?ection of said spring
thereof, said bracket member end wall having a central
beyond the rebound limits established by the static load 50 opening therethrough in substantially axial alignment
clearances.
with the threaded ‘opening of said frame member, a bolt
'8. A vibration isolating mount comprising two support
member of stepped diameter threadably mounted adja
members spaced ‘from each other, at least one of said
members being subjected to vibration inducing forces,
a spring normally supporting the mounted weight applied
between said support members and having a resonant
frequency below the normal frequency range of said vi
bration inducing forces, one of said members having a
recess therein terminating in aperforated end wall, a spool
comprising an intermediate spool portion and two spool
end flanges, said intermediate spool portion extending
through the perforation in said end wall between the two
end ?anges axially spaced on opposite sides of said end
wall, means for adjustably mounting said spool for ax
ial movement on said other member, two resilient grom
mets frictionally and resiliently embracing said interme~
diate spool portion, one of said grommets being mount
ed within said recess and peripherally and resiliently en
cent one end thereof within the threaded opening of said
frame member, said bolt member having a reduced diam
55 eter shank portion de?ning a shoulder with said one end
and extending therefrom through the opening in said
braoket member and being threaded at its opposite end,
a coil spring compressively interposed between said sup
port and bracket member in spaced embracing relation
to said bolt member and to said bracket member de?ned
bosses, said spring supporting the weight of the engine
applied thereto and having a low de?ection rate character
istic and a natural resonant frequency within the engine
cranking and idle speeds, a spool assembly mounted on
said bolt member comprising two end washers and an
intermediate spacer sleeve maintaining said washers in
?xed axially spaced relation on the bolt, a nut member
threadably mounted on the opposite end of said bolt mem—
gaging the surface thereof, said grommets being of lim
her and abutting the adjacent washer member to main
ited axial dimensions and said spool being adjusted ax 70 tain the opposite washer member in abutment with the
ially by its mounting means relative .to said other member
bolt de?ned shoulder, and two resilient grommets fric
to provide predetermined clearances between said grom
tionally
and resiliently embracing said spacer sleeve and
mets and said end wall under static load conditions.
interposed between said washers and said bracket mem
9. In a vibration isolating mount as set forth in claim
8, each of said grommets being beveled inwardly from at 75 ber adjacent the opening therethrough, said grommets be
ing of limited axial dimensions and said bolt and spool
3,052,435
8
7
assembly being adjusted by rotation of said bolt member
and resiliently embracing said spacer sleeve and interposed
to provide predetermined clearances between said grom
mets and said bracket member under static load condi
tions.
12. A resilient vibration and shock isolating device for
between said washers and said bracket end wall within
said bracket de?ned recesses, one of said grommets pe
mounting an internal combustion engine in a motor ve
being spaced radially inwardly of the cylindrical recess
de?ning surface of said bracket boss, said grommets be
ing of limited axial dimensions and said bolt and spool
assembly being adjusted by rotation of said bolt member
to provide predetermined clearances between said grom
ripherally engaging the cylindrical recess de?ning surface
of said bracket sleeve and the other of said grommets
hicle, said engine mounting device comprising a stamped
vehicle frame member, a stamped engine supporting
bracket member spaced from said frame member, said
frame and bracket members having cylindrical bosses
thereon extending in substantial parallel axial alignment
to each other and de?ning opposed parallel end Walls,
mets and said bracket member under static load condi
tions, each of said grommets being beveled inwardly
from the opposite axial ends thereof to an inner surface
said frame member end wall having a threaded opening
of reduced axial dimension in resilient engagement with
centrally therethrough and said bracket member end wall
having a central opening therethrough in substantially 15 the spool assembly sleeve whereby said one grommet pro
vides initial lateral variable rate compressive rebound
axial alignment with the threaded opening of said frame
stability to the mount and is subjected to and provides ini
member, a sleeve member secured to said bracket mem
tial variable rate vibration damping de?ection supple
ber end wall and cooperating therewith to de?ne a cylin
menting the vibration damping de?ection of said spring
drical recess oppositely disposed to that formed by said
bracket member boss, a bolt member of stepped diam 20 within the rebound limits established by the static load
clearances provided between said grommets and end wall,
eter threadably mounted adjacent one end thereof with
said other grommet being subjected to and providing addi
in the threaded opening of said frame member, said bolt
tional variable rate lateral rebound stability to said mount
member having a reduced diameter shank portion de?n
under extreme lateral load conditions, and both of said
ing a shoulder with said one end and extending therefrom
through the opening in said bracket member and being 25 grommets being subjected to and providing variable rate
vibration damping de?ection and compressive rebound
threaded at its opposite end, a coil spring compressively
supplementing vibration damping spring de?ection be
interposed between said support and bracket member in
yond the rebound limits established by the static clear
spaced embracing relation to said bolt member and to
ances.
said bracket member de?ned bosses, said spring support
ing the weight of the engine applied thereto and having a 30
References Cited in the ?le of this patent
UNITED STATES PATENTS
low de?ection rate characteristic and a natural resonant
frequency characteristic lies within the engine cranking
and idle speeds, a spool assembly mounted on said bolt
member comprising two end washers and an intermedi
ate spacer sleeve maintaining said washers in ?xed axial
35
ly spaced relation on the bolt, a nut member threadably
mounted on the opposite end of said bolt member and
abutting the adjacent washer member to maintain the
opposite washer member in abutment with the bolt de
?ned shoulder, and two resilient grommets frictionally 40
1,176,934
1,660,671
1,833,424
Taylor ......a __________ __ Mar. 24, 1916
Gurney ______________ __ Feb. 28, 1928
Jansson _____________ __ Nov. 24, 1931
1,968,040
2,270,335
2,869,811
Houdek _____________ __ July 31, 1934
Parkinson ____________ __ Jan. 20, 1942
Boschi ______________ __ Jan. 20, 1959
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