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Description  |
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BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to an elastic bushing filled with a
viscous fluid, and more particularly to such a fluid-filled elastic
bushing which exhibits an excellent characteristic of damping input
vibrations.
2. Discussion of the Prior Art
As one type of vibration insulator for flexible or elastic connection of a
shaft member of a vibration system to a support structure, there is known
a vibration-isolating bushing such as an elastic bushing which includes a
tubular elastic body which is closed at its one end and open at the other
end. For example, the tubular elastic body is secured to a suitable
support member such as a frame of a front-engine front-drive vehicle
having a strut type front suspension system, such that a shaft member such
as a compression rod which serves as a pivot on the rear side of a L-type
lower arm of the suspension system is fixedly inserted into the bore of
the elastic body. According to this arrangement, the shaft member is
connected to the support member in a vibration isolating or damping
manner, so that the tubular elastic body restrains displacements of the
shaft member in one of its opposite axial directions and in its radial
direction.
The elastic bushing having the conventional construction employing a single
formed rubber mass as the elastic body as described above is uncapable of
providing a sufficient damping effect with respect to vibrations applied
thereto. In particular, it has been difficult to provide the conventional
elastic bushing with excellent damping characteristic to input vibrations
which has a comparatively low frequency range.
Where the elastic bushing is used as a vibration-isolating bushing for
flexibly connecting the compression rod of the L-type lower arm of the
vehicle front suspension system to the vehicle frame,, the elastic body
suffers from low vibration damping characteristic with respect to
vibrations which are applied in the radial direction of the bushing,
particularly where the frequency of the vibrations falls within a range of
approximately 10-15 Hz, which is the resonance frequency of the suspension
system. Hence, the elastic bushing is uncapable of effectively preventing
shimmy vibrations of the vehicle in running, which have an adverse effect
on the steering and running stabilities of the vehicle. Thus, the known
elastic bushing has a problem that should be solved.
SUMMARY OF THE INVENTION
It is accordingly an object of the present invention to provide an elastic
bushing filled with a viscous fluid, which is capable of providing
improved vibration damping and isolating characteristic with respect to
vibrations applied in both axial and radial directions thereof.
The above object may be achieved according to the principle of the present
invention, which provides an elastic bushing filled with a viscous fluid,
for flexible connection of a shaft member to a support structure,
comprising: (a) a tubular inner sleeve which is closed at one of opposite
axial ends thereof and open at the other end, the shaft member being
fixedly inserted in the inner sleeve; (b) a tubular outer sleeve which is
closed at one of opposite axial ends thereof and open at the other end,
and which is disposed radially outwardly of the inner sleeve such that an
annular space is formed between an outer circumferential surface of the
inner sleeve and an inner circumferential surface of the outer sleeve and
such that a cylindrical space is formed between opposed surfaces of bottom
walls at the closed ends of the inner and outer sleeves, the outer sleeve
being secured to the support structure; (c) a cylindrical elastic
connecting member which fluid tightly fills a portion of the annular space
adjacent to the open ends of the inner and outer sleeves, and thereby
cooperate with the inner and outer sleeves to define a fluid chamber which
includes a remaining portion of the annular space and the cylindrical
space, the fluid chamber being filled with the fluid; and (d) a first
elastic operating member formed on one of the outer and inner
circumferential surfaces of the inner and outer sleeves, so as to occupy a
part of the remaining portion of the annular space and cooperate with the
other of the outer and inner circumferential surfaces to define
therebetween an annular first restricted portion of the fluid chamber.
Preferably, the instant elastic bushing further comprises a second elastic
operating member formed on one of the opposed surfaces of the bottom walls
of the inner and outer sleeves, so as to occupy a part of the cylindrical
space and cooperate with the other of the opposed surfaces to define
therebetween a planar second restricted portion of the fluid chamber which
extends in a radial direction of the bushing.
In the fluid-filled elastic bushing of the present invention constructed as
described above, the masses of the viscous fluid existing in the first and
second restricted portions of the fluid chamber are subject to shearing
stresses when the first and second elastic operating members are
oscillated in the radial and axial directions of the bushing, upon radial
and axial relative displacements of the inner and outer sleeves due to
vibrations applied to the bushing in the radial and axial directions.
However, the viscosity of the fluid masses provides a resistance to those
shearing stresses, which results in effectively damping the input radial
and axial vibrations. This damping effect obtained based on the viscosity
of the fluid in the restricted portions of the fluid chamber is added to a
damping effect which is offered by the elastic connecting member disposed
between the inner and outer sleeves. Hence, the instant fluid-filled
elastic bushing exhibits improved vibration damping and insulating
characteristic, in particular, better damping effect, than the
conventional elastic bushing which merely employs a formed elastic body
between the inner and outer sleeves.
In one form of the present invention, the elastic bushing further comprises
a metal sleeve fitted on an outer circumferential surface of the
cylindrical elastic connecting member, and a rubber layer formed on a
portion of the inner circumferential surface of the outer sleeve adjacent
to the open end thereof. In this case, the metal sleeve is held in pressed
abutting contact with the rubber layer, so as to maintain fluid tightness
of the fluid chamber. The rubber layer may have a plurality of sealing
lips which are spaced part from each other in an axial direction of the
bushing.
In another form of the invention, the cylindrical elastic connecting member
and the first and second elastic operating members constitute an
integrally formed elastic body which is secured by vulcanization of an
unvulcanized rubber material to the inner sleeve, in a suitably prepared
mold.
In a further form of the invention, the bottom wall of the outer sleeve has
a plurality of fluid injecting holes through which the fluid is introduced
into the fluid chamber. In this case the fluid chamber may be filled after
the elastic bushing is assembled with the fluid chamber left unfilled.
However, the fluid chamber may be filled with the fluid, during assembling
of the bushing within a mass of the fluid.
In a still further form of the invention, the outer sleeve has a stepped
cylindrical wall which has the inner circumferential surface that
partially define the annular space. The stepped cylindrical wall includes
a large-diameter portion adjacent to the open end of the outer sleeve and
a small-diameter portion adjacent to the bottom wall thereof.
According to one arrangement of the above form of the invention, the
bushing further comprises a mounting rubber sleeve formed on the
small-diameter portion of the stepped cylindrical wall of the outer
sleeve. In this instance, the outer sleeve is secured to the support
structure via the mounting rubber sleeve.
According to another arrangement of the same form of the invention, the
outer sleeve includes an outward flange which extends radially outwardly
from the open end of the outer sleeve and engages the support structure.
In this case, the outward flange may consist of a semi-cylindrical flange
formed over a substantially half of the circumference of the outer sleeve,
and the bushing may further comprise the mounting rubber sleeve as
indicated above. In this case, the mounting rubber sleeve may include a
semi-cylindrical flange portion at one of opposite axial ends thereof
which is adjacent to the closed end of the outer sleeve. The
semi-cylindrical flange portion is formed so as to face the
semi-cylindrical flange of the outer sleeve. In the present arrangement,
the outer sleeve is secured to the support structure such that a part of
the support structure is positioned between the semi-cylindrical flange
portion of the mounting rubber sleeve and the semi-cylindrical flange of
the outer sleeve. It is desirable that the surface of the semi-cylindrical
flange of the outer sleeve which faces the semi-cylindrical flange portion
of the mounting rubber sleeve is covered by a rubber layer, so that the
support structure is held in pressed contact with the rubber layer and the
semi-cylindrical flange portion of the mounting rubber sleeve.
In a yet further form of the present invention, the annular first
restricted portion of the fluid chamber has a clearance of 1-6 mm as
measured between the first elastic operating member and the opposite outer
or inner circumferential surface of the inner or outer sleeves. Similarly,
the planar second restricted portion of the fluid chamber has a clearance
of 1-6 mm as measured between the second elastic operating member and the
opposite bottom wall of the inner o outer sleeve.
To practice the principle of the invention, it is generally desirable that
the fluid chamber be filled with the fluid whose kinematic viscosity is at
least 1000 centistokes, preferably at least 10,000 centistokes, and most
preferably within a range of 100,000 and 1,000,000 centistrokes.
BRIEF DESCRIPTION OF THE DRAWINGS
The above and optional objects, features and advantages of the present
invention will become more apparent by reading the following detailed
description of a presently preferred embodiment of the invention, when
considered in connection with the accompanying drawings, in which:
FIG. 1 is an elevational view in axial cross section of one embodiment of a
fluid-filled elastic bushing of this invention, taken along line I--I of
FIG. 2;
FIG. 2 is a right-hand side end elevational view of the elastic bushing of
FIG. 1;
FIG. 3 is a cross sectional view taken along line III--III of FIG. 2;
FIG. 4 is an elevational view in axial cross section of an intermediate
product prepared in a vulcanization process, for manufacturing the instant
elastic bushing, the cross sectional view being taken along line IV--IV of
FIG. 5;
FIG. 5 is a right-hand side end elevational view of the intermediate
product of FIG. 4;
Fi. 6 is an elevational view in axial cross section of a outer sleeve unit
of the elastic bushing of FIG. 1, taken along line VI--VI of FIG. 7;
FIG. 7 is a right-hand side end elevational view of the outer sleeve unit
of FIG. 6; and
FIG. 8 is a cross sectional view taken along line VIII--VIII of FIG. 7.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring first to FIGS. 1-3, there is shown the presently preferred form
of the fluid-filled elastic bushing in the form of an elastic bushing
adapted for elastic or flexible connection of a compression rod of an
L-type lower arm of the front suspension system of a motor vehicle to a
frame of the vehicle.
As indicated in these figures, the elastic bushing includes a tubular
metallic inner sleeve 10 which is closed at one of its axial ends and open
at the other end, and a tubular metallic outer sleeve 12 which surrounds
the inner sleeve 10 such that an annular space is formed between the outer
circumferential surface of the inner sleeve 10 and the inner
circumferential surface of the outer sleeve 12. These inner and outer
sleeves 10, 12 are elastically secured to each other by a generally
tubular elastic body 14 such that a cylindrical space communicating with
the above-indicated annular is left between the closed end portion of the
outer sleeve 12 and the corresponding end portion of the elastic body 14.
The elastic bushing is installed on the vehicle such that an end portion of
the compression rod of the L-type lower arm is fixedly inserted into the
axial bore of the inner sleeve 10, while the outer sleeve 12 is secured to
the vehicle frame by using a U-shaped mounting bracket.
In the process of manufacturing the instant elastic bushing, there is
prepared an intermediate product as shown in FIGS. 4 and 5, such that the
elastic body 14 is secured to the inner sleeve 10 by vulcanization in a
suitable mold.
The elastic body 14 is an integrally formed rubber mass which includes a
cylindrical elastic connecting member 18, a cylindrical first elastic
operating member 20 integrally connected to the elastic connecting member
18, and a disc-like second elastic operating member 22 formed integrally
with the first elastic operating member 20. The cylindrical elastic
connecting member 18 is formed on a portion of the outer circumferential
surface of a cylindrical wall 17 of the inner sleeve 10, which is adjacent
to its open end. The cylindrical first elastic operating member 20 is
formed on the rest of the outer circumferential surface of the cylindrical
wall 17, which is adjacent to a bottom wall 19 of the inner sleeve 10. The
disc-like second elastic operating member 22 is formed on the outer
surface of the bottom wall 19 of the inner sleeve 10.
On the outer circumferential surface of the cylindrical elastic connecting
member 18 of the elastic body 14, there is secured a metal sleeve 26 such
that the inner sleeve 10 and the metal sleeve 26 are coaxial with each
other. This metal sleeve 26 has a semi-annular outward flange 24 which
extends radially outwardly from one of its opposite axial ends that is
adjacent to the open end of the inner sleeve 10. The outward flange 24
corresponds to a substantially half of the circumference of the inner
sleeve 10, and is aligned with the open end of the inner sleeve 10.
To prepare the intermediate product 16, the inner sleeve 10 and the metal
sleeve 26 are positioned in place in the mold, and an unvulcanized rubber
material is introduced into the mold, so as to form the elastic body 14 by
vulcanization of the unvulcanized rubber material as well known in the
art. In the present embodiment, the cylindrical wall 17 of the inner
sleeve 10 has a plurality of holes, which permit the unvulcanized rubber
material to flow from the outside into the inside of the wall 17, so that
the inner circumferential surface of the wall 17 is coated with a thin
inner rubber layer 28.
The thus prepared intermediate product 16 is pre-loaded with a suitable
amount of radially inward compressive force, which is given, for example,
by using eight drawing dies disposed around the metal sleeve 26.
The outer sleeve 12, which is prepared separately from the intermediate
product 16, has a semi-cylindrical outward flange 30 which extends
radially outwardly from its open end, as illustrated in FIGS. 6-8. The
outward flange 30 corresponds to a substantially half of the circumference
of the sleeve 12, and is provided at its circumferential ends with a pair
of caulking portions 32.
The outer sleeve 12 has a stepped cylindrical wall 34 which consists of a
small-diameter portion 40 on the side of its closed end, and a
large-diameter portion 44 on the side of its open end. The large-diameter
portion 44 has a suitable axial dimension considerably smaller than that
of the small-diameter portion 40.
On the outer surface of the small-diameter portion 40 of the stepped
cylindrical wall 34, there is formed a mounting rubber sleeve 42 by
vulcanization. As indicated in FIG. 7, one of two halves of the
circumference of the rubber sleeve 42 which corresponds to the half of the
circumference of the outer sleeve 12 that is not provided with the
semi-cylindrical outward flange 30 has a generally trapezoidal outer
profile which fits a positioning recess formed in the vehicle frame. On
the other hand, the other half of the circumference of the rubber sleeve
42 has an arcuate outer profile and has a flange portion 48 formed at the
axial end adjacent to the bottom wall 36 of the outer sleeve 12. As
indicated in FIG. 8, the flange portion 48 faces the outward flange 30 of
the outer sleeve 12, in the axial direction of the sleeve 12. For
installation of the instant elastic bushing, the above-indicated U-shaped
mounting bracket secured to the vehicle frame is fitted on the mounting
rubber sleeve 42, as described later. The axially inner surface of the
outward flange 30 which faces the flange portion 48 is covered by a rubber
layer 50 having a suitable thickness, so that the appropriate end of the
mounting bracket is held in abutting contact with the rubber layer 50.
The inner surface of the large-diameter portion 44 of the stepped
cylindrical wall 34 of the outer sleeve 12 is covered by a sealing rubber
sleeve 46 formed by vulcanization. This rubber sleeve 46 has two
circumferential sealing lips 52, 52 formed on its inner surface.
The instant elastic bushing is obtained by forcing the intermediate product
of FIG. 4 into the thus constructed outer sleeve 12, through the open end
of the sleeve 12, bending the caulking portions 32 of the sleeve 12
against the outward flange 24 of the intermediate product 16, and
subjecting the large-diameter portion 44 of the outer sleeve 12 to a
preliminary radially inward compressing operation using for example eight
drawing dies disposed around the large-diameter portion 44.
With the intermediate product 16 forced into the interior of the outer
sleeve 12, the inner sleeve 10 is disposed coaxially with the outer sleeve
12, such that the two sleeves 10, 12 are radially spaced apart from each
other by a predetermined distance by the elastic body 14 which fluid
tightly fills a portion of the annular space between the two sleeves 10,
12 that is adjacent to their open ends, as shown in FIGS. 1-3. Described
more specifically, the inner and outer sleeves 10, 12 and the elastic body
14 cooperate to define a fluid chamber 54. This fluid chamber is sealed at
the open end portion of the inner or outer sleeve 10, 12, by the
cylindrical elastic connecting member 18 of the elastic member 14
integrally secured to the inner sleeve 10. More precisely, the fluid
tightness of the fluid chamber 54 is maintained by a pressed contact
between the outer surface of the metal sleeve 26 intergrally secured to
the elastic connecting member 18 and the sealing rubber sleeve 46
integrally secured to the outer sleeve 12.
In the thus constructed elastic bushing, the wall thickness of the
cylindrical first elastic operating member 20 of the elastic body 14 is
determined such that its outer circumferential surface is spaced from the
inner circumferential surface of the outer sleeve 12 by a suitable
distance so that the fluid chamber 54 includes a first restricted portion
in the form of an annular space 56 defined between the first elastic
operating member 20 and the outer sleeve 12, as illustrated in FIGS. 1 and
3. In other words, the first elastic operating member 20 occupies a part
of the annular space left between the inner and outer sleeves 10, 12 and
thereby cooperate with the outer sleeve 12 to define therebetween the
annular space 56 of the fluid chamber 54.
Similarly, the thickness of the disc-like second elastic operating member
22 of the elastic body 14 is determined such that its outer circular flat
surface is spaced from the inner surface of a circular raised portion 38
of the bottom wall 36 of the outer sleeve 12 by a suitable distance so
that the fluid chamber 54 includes a second restricted portion in the form
of a relatively thin planar or flat space 58 which is defined between the
second elastic operating member 20 and the raised portion 38, so as to
extend in the radial direction of the bushing. Namely, the second elastic
operating member 22 occupies a part of the cylindrical space left between
the bottom walls 19, 36 of the inner and outer sleeves 10, 12, and thereby
cooperates with the raised portion 38 of the bottom wall 36 of the outer
sleeve 12 to define therebetween the planar space 58.
The first and second elastic operating members 20, 22 of the elastic body
14 which cooperate with the closed end portion of the outer sleeve 12 to
define the annular and thin flat spaces 56, 58 are formed substantially
mechanically independently of the elastic connecting member 18, so as to
minimize elastic deformation of the elastic operating members 20, 22 upon
elastic deformation of the elastic connecting member 18 due to a relative
radial displacement of the inner and outer sleeves 10, 12.
The fluid chamber 54 which includes the first and second restricted
portions in the form of the annular space 56 and the thin flat space 58 is
filled with a suitable viscous fluid. In the instant elastic bushing, the
bottom wall 36 of the outer sleeve 12 has two fluid injecting holes 60, 60
as shown in FIGS. 7 and 8. These holes 60 are used to fill the viscous
fluid into the fluid chamber 54 after the intermediate product 16 is fluid
tightly fitted in the outer sleeve 12 as described above. For instance,
the fluid is injected into the fluid chamber 54 through one of the two
holes 60, 60 while the other hole 60 is used as an air breather through
which the atmosphere in the chamber 54 is discharged as the fluid is
introduced into the chamber 54. With the fluid chamber 54 filled with the
fluid, the holes 60 are fluid tightly closed by suitable closure means
such as rivet plugs 62, 62 as shown in FIG. 3. Thus, the fluid-filled
elastic bushing as shown in FIGS. 1-3 is manufactured.
As previously stated, the instant elastic bushing is installed on the
vehicle such that the compression rod of the L-type lower arm of the front
suspension system is fixedly inserted into the bore of the inner sleeve
10, while the outer sleeve 12 is secured to the vehicle frame via the
U-shaped bracket. In this manner, the compression rod is flexibly or
elastically connected to the vehicle frame.
When a relative radial displacement of the inner and outer sleeves 10, 12
occurs due to a vibrational load applied to the thus constructed
fluid-filled elastic bushing in the radial direction, the first elastic
operating member 20 formed on the cylindrical wall 17 of the inner sleeve
10 is oscillated radially in the fluid chamber 54 relative to the inner
circumferential surface of the cylindrical wall 34 of the outer sleeve 12.
At the same time, the second elastic operating member 22 formed on the
bottom wall 19 of the inner sleeve 10 is oscillated relative to the inner
surface of the circular raised portion 38 of the bottom wall 36 of the
outer sleeve 12 in the radial direction of the bushing. As a result, the
masses of the viscous fluid existing in the first and second restricted
portions (annular space 56 and thin flat space 58) of the fluid chamber 54
are subject to shearing stresses. In other words, the viscosity of the
fluid masses in these restricted portions 56, 58 provides resistances to
the shearing stresses due to the radial movements of the first and second
elastic operating members 20, 22.
When a relative axial displacement of the inner and outer sleeves 10, 12
occurs due to a vibrational load applied to the instant elastic bushing in
the axial direction, the first elastic operating member 20 formed on the
cylindrical wall 17 is oscillated in the fluid chamber 54 in the axial
direction of the inner sleeve 10 relative to the cylindrical wall 34 of
the outer sleeve 12. Simultaneously, the second elastic operating member
22 formed on the bottom wall 19 of the inner sleeve 10 is oscillated
toward and away from the raised portion 38 of the bottom wall 36 of the
outer sleeve 12. Consequently, the masses of the viscous fluid existing in
the first and second restricted portions 56, 58 of the fluid chamber 54
are subject to shearing stresses. In this case, too, the viscosity of the
fluid masses in these restricted portions 56, 58 provides resistances to
the shearing stresses due to the axial movements of the first and second
elastic operating members 20, 22.
A value (F) of the resistance to the shearing stresses due to the viscosity
of the fluid masses is expressed by the following equation:
F=(.mu.A/h)v
where,
.mu.: coefficient of viscosity of the fluid
h: clearance between the first (second) elastic operating member 20 (22)
and the outer sleeve 12, at the annular space 56 (flat space 58)
v: velocity of the vibrational load
It follows from the above equation that the resistance force (F) produced
by the viscous fluid depends upon the velocity of the input vibration, and
is substantially free from an influence of the frequency of the vibration.
That is, the instant fluid-filled elastic bushing exhibits a excellent
damping characteristic owing to the effective resistance force produced by
the fluid masses due to its viscosity, with respect to the input
vibrations in a relatively wide frequency range, which includes the
vibrations in a comparatively low frequency band that cannot be dealt with
in an effective manner by elastic properties of a single formed rubber
mass used in the conventional elastic bushing. Accordingly, the instant
fluid-filled elastic bushing is capable of preventing shimmy vibrations of
the vehicle, and effectively enhancing the steering and running stability
of the vehicle.
It will be understood from the above description that the kinematic
viscosity of the fluid filling the fluid chamber 54, and the clearances
"h" of the annular and flat spaces 56, 58 may be determined so as to
provide the elastic bushing with desired damping characteristic. For
instance, it is possible to use a silicone oil or other fluid which has a
kinematic viscosity of at least 1000 centistokes, preferably at least
10,000 centistokes, and more preferably within a range of
100,000-1,000,000 centistokes. The clearances "h" at the first and second
restricted portions 56, 58 of the chamber 54 should generally be held
within a range of 1-6 mm.
In the thus constructed fluid-filled elastic bushing, the first and second
elastic operating members 20, 22 which partially define the first and
second restricted portions (annular and flat spaces) 56, 58 also function
as elastically yieldable members which may abut on the inner surfaces of
the outer sleeve 12, thereby preventing excessive amounts of relative
radial and axial displacements of the inner and outer sleeves upon
application of an excessive vibrational load to the bushing.
A further advantage of the present fluid-filled elastic bushing is offered
by the provision of the fluid injecting holes 60, 60 formed in the bottom
wall 36 of the outer sleeve 12. Namely, the holes 60, 60 facilitate the
filling of the viscous fluid chamber 54 with the selected fluid, after the
intermediate product 16 is forced into the outer sleeve 12. This manner of
filling the fluid chamber 54 eliminates undesirable exposure of the outer
surface of the elastic bushing to the fluid, which would be encountered if
the fluid chamber 54 was filled with the fluid by assembling the
intermediate product 16 and the outer sleeve 12, within a mass of the
fluid. Accordingly, the manufacturing process of the instant bushing is
comparatively simplified.
While the presently preferred embodiment of the fluid-filled elastic
bushing of the present invention has been described, for illustrative
purpose only, it is to be understood that the invention is not limited to
the details of the illustrated embodiment.
In the illustrated embodiment, the cylindrical first elastic operating
member 20 and the disc-like second elastic operating member 22 ar formed
as integral parts of the cylindrical elastic connecting portion 18 of the
elastic body 14. However, the elastic operating members 20, 22 may be
formed separately from the elastic connecting member 18. In this case, the
members 20, 22 may be given elastic properties different from that of the
connecting member 18.
Further, the first and second elastic operating members 20, 22 may be
replaced by respective elastic members which are formed on the inner
surfaces of the outer sleeve 12 such that these members cooperate with the
inner sleeve 10 to define first and second restricted portions of the
fluid chamber 54.
While the illustrated elastic bushing has the fluid injecting holes 60, 60
formed through the bottom wall 36 of the outer sleeve 12 for filling the
fluid chamber 54 with the viscous fluid, the filling of the fluid chamber
54 may be accomplished by assembling the inner and outer sleeves 10, 12
within a mass of the fluid.
Further, the inner rubber layer 28 formed on the inner circumferential
surface of the inner sleeve 10 and the mounting rubber sleeve 42 formed on
the outer circumferential surface of the outer sleeve 12 are not essential
to practice the principle of the present invention, and the configurations
of these rubber layer and sleeve 28, 42 may be modified as needed,
depending upon the specific configurations of the appropriate compression
rod and mounting bracket.
Although the illustrated fluid-filled elastic bushing is adapted for
elastic connection of the compression rod of the L-type lower arm of the
front suspension system of a vehicle to the vehicle frame, the elastic
bushing of the present invention may be equally suitably used as a bushing
interposed between any two members of a vibration system. In this case,
necessary changes and modifications may obviously be made in the
construction of the bushing.
It will be understood that the present invention may be embodied with
various other changes, modifications and improvements which may occur to
those skilled in the art, without departing from the spirit and scope of
the invention defined in the following claims.
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