Cylindrical elastic mount with vibration damper including cylindrical rigid split member

A cylindrical elastic mount with a vibration damper, including radially spaced-apart inner and outer sleeves, an elastic body interposed between the inner and outer sleeves so as to elastically connct the two sleeves, and a generally cylindrical rigid split member disposed between the inner and outer sleeves and elasticallly supported by the two sleeves through the elastic body, such that the elastic body is divided by the rigid split member into radially inner and outer portions. The rigid split member and the elastic body cooperate with each other to provide the vibration damper. The generally cylindrical rigid split member consists of a plurality of rigid segments which are embedded in the elastic body such that adjacent segments of the plurality of rigid segments abut on each other at circumferentially opposed end faces thereof so as to assume a generally cylindrical shape. The radially outer portion of the elastic body is radially inwardly compressed between the outer sleeve and the rigid split member while the radially inner portion is radially inwardly compressed between the rigid split member and the inner sleeve.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates generally to a cylindrical elastic mount 
including a dynamic vibration damper, and more particularly to such a 
cylindrical elastic mount which can be produced with improved efficiency 
and is thus available at a reduced cost of manufacture. 
2. Discussion of the Prior Art 
A cylindrical elastic mount is known as a device for elastically or 
flexibly connecting two members in a vibration system in a vibration 
damping or isolating manner, or as a device for mounting one of the two 
members on the other member such that the one member is elastically or 
flexibly supported by the other member. Examples of such a cylindrical 
elastic mount are disclosed in laid-open publication No. 56-63141 of 
unexamined Japanese patent application, and laid-open publication No. 
57-59119 of unexamined Japanese utility model application. The cylindrical 
elastic mount disclosed in these publications has an inner and an outer 
sleeve which are made of a metallic material and are disposed in radially 
spaced-apart, coaxial or non-coaxial relationship with each other. Between 
these inner and outer sleeves, there is interposed an elastic body such as 
a formed rubber mass, such that the two sleeves are elastically connected 
by the elastic body. The cylindrical elastic mount of this type is widely 
used as an engine mount adapted for use on a transverse front-engine 
front-drive (F-F) car, and as a body mount or a suspension bushing for a 
motor vehicle, for example. 
As one type of the elastic mount as described above, there is known a 
cylindrical elastic mount having a dynamic vibration damper which consists 
of the elastic body, and a rigid member which is disposed between the 
inner and outer sleeves. This rigid member is embedded in or secured to 
the elastic body by means of vulcanization, and is supported by the inner 
and outer sleeves through the elastic body. In the presence of this 
dynamic vibration damper, the elastic mount exhibits a relatively low 
dynamic spring constant with respect to a middle- to high-frequency range 
of input vibrations. Although the rigid member included in the elastic 
mount may be a block-like member, it is preferable to employ a cylindrical 
rigid member which is disposed between the inner and outer sleeves so as 
to extend over the entire circumference of the mount. The use of the 
cylindrical member as the rigid member makes it easy to tune the dynamic 
spring characteristics of the elastic mount, and permits the elastic mount 
to provide an excellent damping effect with respect to the input 
vibrations applied in any radial direction. 
When the cylindrical rigid member is provided between the inner and outer 
sleeves, the inner sleeve, the cylindrical rigid member and the outer 
sleeve are disposed in this order as viewed in a radially outward 
direction of the mount. Then, a radial spacing between the inner sleeve 
and the cylindrical rigid member and a radial spacing between the 
cylindrical rigid member and the outer sleeve are filled with respective 
masses of a suitable rubber material, so as to form radially inner and 
outer portions of the elastic body on the opposite sides of the 
cylindrical rigid member. In this case, when the outer sleeve is radially 
inwardly compressed after the elastic body is formed by vulcanization, it 
is practically impossible to give a suitable degree of preliminary radial 
compression to the radially inner portions of the elastic body interposed 
between the inner sleeve and the cylindrical rigid member. 
In view of the above, the cylindrical rigid member is conventionally 
composed of radially inner and outer metallic members each having a 
cylindrical shape. More specifically, the conventional elastic mount 
consists of an inner bushing which has a first elastic body interposed 
between the inner sleeve and the inner metallic member for elastic 
connection therebetween, and an outer bushing which has a second elastic 
body interposed between the outer sleeve and the outer metallic member for 
elastic connection therebetween. After these inner and outer bushings are 
separately formed, the inner metallic member is radially inwardly 
compressed so that a suitable degree of preliminary radial compression is 
given to the first elastic body of the inner bushing. Similarly, the outer 
sleeve is radially inwardly compressed so that a suitable degree of 
preliminary radial compression is given to the second elastic body of the 
outer bushing. Thereafter, the outer metallic member of the outer bushing 
is fixedly fitted on the inner metallic member of the inner bushing, so as 
to provide an integrally formed bushing structure. In this manner, the 
intended cylindrical elastic mount with a vibration damper can be 
obtained. 
In manufacturing the thus constructed cylindrical elastic mount, however, 
two tubular metallic members are needed for providing the cylindrical 
rigid member, and the inner and outer bushings must be prepared by 
respective vulcanizing operations for forming the first and second elastic 
bodies, and by respective drawing operations in which the inner metallic 
member and the outer sleeve are radially inwardly compressed. Further, the 
inner and outer bushings which are separately produced at different sites 
must be put together at an assembly site. Thus, the cylindrical elastic 
mount of the above type is manufactured with considerably low efficiency, 
at a relatively high cost, owing to a relatively large number of process 
steps required for forming the two independent bushings and assembling 
these bushings together. Further, this elastic mount requires two tubular 
metallic members, which also push up the cost of manufacture of the mount. 
SUMMARY OF THE INVENTION 
The present invention was developed in view of the drawback encountered in 
the prior art discussed above. It is therefore a first object of the 
present invention to provide a cylindrical elastic mount with a vibration 
damper including a generally cylindrical rigid member, which is simple in 
construction, and is economical to manufacture with significantly improved 
efficiency. 
A second object of the present invention is to provide a method suitable 
for manufacturing such a cylindrical elastic mount as indicated above. 
The above first object may be achieved according to the principle of the 
present invention, which provides a cylindrical elastic mount with a 
vibration damper comprising: (a) an inner and an outer sleeve which are 
disposed in spaced-apart relation with each other in a radial direction of 
the mount; (b) an elastic body interposed between the inner and outer 
sleeves so as to elastically connect the inner and outer sleeves; and (c) 
a generally cylindrical rigid split member disposed between the inner and 
outer sleeves and elastically supported by the inner and outer sleeves 
through the elastic body, such that the elastic body is divided by the 
rigid split member into radially inner and outer portions, the rigid split 
member and the elastic body cooperating with each other to provide the 
vibration damper. The generally cylindrical rigid split member consists of 
a plurality of rigid segments which are embedded in the elastic body such 
that adjacent segments of the plurality of rigid segments abut on each 
other at circumferentially opposed end faces thereof so as to assume a 
generally cylindrical shape. The radially outer portion of the elastic 
body is radially inwardly compressed between the outer sleeve and the 
rigid split member while the radially inner portion is radially inwardly 
compressed between the rigid split member and the inner sleeve. 
The second object may be achieved according to a second aspect of the 
present invention, which provides a method of manufacturing a cylindrical 
elastic mount having an inner and an outer sleeve which are disposed in 
spaced-apart relation with each other in a radial direction of the mount, 
and an elastic body interposed between the inner and outer sleeves so as 
to elastically connect the inner and outer sleeves, comprising (a) the 
steps of embedding a plurality of substantially arcuate rigid segments in 
the elastic body such that the rigid segments are spaced apart from each 
other in a circumferential direction of the mount, with a predetermined 
clearance left between circumferentially opposed end faces of adjacent 
ones of the substantially arcuate rigid segments, and (b) radially 
inwardly compressing the outer sleeve so that the substantially arcuate 
rigid segments are brought into abutting contact with each other at the 
circumferentially opposed end faces, so as to provide a generally 
cylindrical rigid split assembly, which is embedded in the elastic body 
such that the elastic body is divided by the rigid split assembly into a 
radially outer portion which is radially inwardly compressed between the 
outer sleeve and the rigid split assembly, and a radially inner portion 
which is radially inwardly compressed between the rigid split assembly and 
the inner sleeve. 
When the present cylindrical elastic mount is constructed as described 
above according to the present invention, the rigid segments for the 
generally cylindrical rigid split member or assembly are moved toward each 
other in radial directions as the diameter of the outer sleeve is reduced 
by a radially inward drawing operation, so that the preliminary 
compression is effectively given to the radially inner portion of the 
elastic body as well as to the radially outer portion. After the rigid 
segments abut on each other to form the generally cylindrical rigid split 
assembly, an increase in the compressive force applied to the outer sleeve 
acts on the radially outer portion of the elastic body, so that a suitable 
degree of preliminary compression is given to the radially outer portion 
of the elastic body between the outer sleeve and the rigid split member. 
In the above arrangement, the present elastic mount need not have the 
conventional two-part structure which includes two independently prepared 
bushings, but may be prepared as a single integral unit formed by 
vulcanization of a rubber material such that the inner and outer sleeves 
and the rigid segments of the rigid split member are integrally connected 
to each other by the elastic body of the rubber material. Accordingly, the 
present elastic mount may be manufactured by only one vulcanizing 
operation for forming the integral unit, and only one drawing operation in 
which the preliminary compression is effectively given to both of the 
radially inner and outer portions of the elastic body. Further, the 
generally cylindrical rigid split member may be formed from a plurality of 
metallic sheet members, which can be pressed into the rigid segments, 
rather than an expensive tubular member or members. Thus, the present 
cylindrical elastic mount with a vibration damper is considerably simple 
in construction, and can be manufactured with significantly high 
efficiency, at a relatively low cost. 
The generally cylindrical rigid split member may have at least one hole 
formed through the thickness thereof, so that the radially inner and outer 
portions of the elastic body are integrally connected to each other 
through the at least one hole. 
The elastic body may have at least one inner void formed in the radially 
inner portion, and at least one outer void formed in the radially outer 
portion, such that the inner and outer voids are located adjacent to 
corresponding circumferential ends of the adjacent segments, and such that 
the inner and outer voids extend in an axial direction of the elastic 
mount. 
Further, the elastic body may have an axial void which is formed in the 
radially inner portion so as to extend in an axial direction of the 
elastic mount over a substantially entire axial length of the elastic 
body. This axial void has a generally arcuate shape in cross section. 
The generally cylindrical rigid split member may consist of a pair of 
semicylindrical members as the plurality of rigid segments which abut on 
each other at circumferentially opposed end faces thereof, such that each 
of the pair of semicylindrical members extends in a circumferential 
direction of the mount along a corresponding half of an inner 
circumferential surface of the outer sleeve. Each of the semicylindrical 
members may have an axial length which is larger than that of the elastic 
body, and extends through the elastic body in an axial direction of the 
elastic mount. The pair of semicylindrical members may be disposed such 
that a plane including the mutually abutting circumferentially opposed end 
faces is substantially perpendicular to a direction in which a vibrational 
load is primarily applied to the elastic mount. 
The present cylindrical elastic mount may be constructed such that a radial 
distance between the inner sleeve and the generally cylindrical rigid 
split member is larger than a radial distance between the outer sleeve and 
the generally cylindrical rigid split member. 
The present cylindrical elastic mount may be constructed such that the 
inner and outer sleeves are eccentrically offset from each other in a 
diametric direction in which a vibrational load is primarily applied to 
the elastic mount. 
The radially outer portion of the elastic body may be radially inwardly 
compressed by radially inwardly drawing the outer sleeve of an 
intermediate product of the elastic mount wherein the circumferentially 
opposed end faces of the adjacent segments of the generally cylindrical 
rigid split member are spaced apart from each other by a predetermined 
distance in a circumferential direction of the mount. In this case, the 
circumferentially opposed end faces are brought into abutting contact with 
each other when the outer sleeve is radially inwardly drawn, whereby the 
radially inner portion of the elastic body is radially inwardly compressed 
.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
Referring first to FIGS. 1 and 2, there is shown a cylindrical elastic 
engine mount with a vibration damper adapted for use on a front-engine 
front-drive (F-F) car. In these figures, reference numerals 10 and 12 
denote an inner and an outer sleeve which are made of metal and are 
radially spaced apart from each other. The inner and outer sleeves 10, 12 
are disposed such that the two sleeves 10, 12 are eccentric with respect 
to each other by a predetermined offset distance in a diametric direction 
in which vibrations are primarily received by the engine mount. Between 
the inner and outer sleeves 10, 12, there is interposed an elastic body 14 
such that the two sleeves 10, 12 are elastically connected to each other 
by the elastic body 14. 
In use, the engine mount is installed on the car such that one of the inner 
and outer sleeves 10, 12 is connected to the body of the car while the 
other sleeve 10, 12 is fixed to an engine unit of the car, so that the 
engine unit is elastically or flexibly mounted on the car body via the 
engine mount. With the engine mount installed in position on the car, the 
weight of the engine unit acts on the inner or outer sleeve 10, 12, 
whereby the two sleeves 10, 12 are displaced relative to each other, with 
elastic deformation of the elastic body 14, in the diametric direction 
(vertical direction as viewed in FIG. 1) in which the two sleeves 10, 12 
are originally eccentric with respect to each other. With the relative 
displacement of the inner and outer sleeves 10, 12 due to the weight of 
the engine unit, the two sleeves 10, 12 are held in substantially coaxial 
or concentric relation with each other. A dynamic vibrational load is 
applied to the present engine mount thus installed on the car, primarily 
in the above-indicated diametric direction in which the inner and outer 
sleeves 10, 12 are eccentrically offset from each other. This direction is 
hereinafter referred to as "load-receiving direction" of the engine mount. 
The inner sleeve 10 is a cylindrical member having a comparatively large 
wall thickness. The outer sleeve 12 is a relatively thin-walled 
cylindrical member having a larger diameter than that of the inner sleeve 
10. This outer sleeve 12 is disposed radially outwardly of the inner 
sleeve 10 such that the outer sleeve 12 is eccentric with respect to the 
inner sleeve 10, by a suitable radial distance. The elastic body 14 is a 
generally annular member having a comparatively large wall thickness. The 
inner and outer sleeves 10, 12 and the elastic body 14 cooperate to 
constitute an integral unit 16, as shown in FIGS. 3 and 4. This integral 
unit 16 is prepared as an intermediate product during manufacture of the 
engine mount, by vulcanizing an unvulcanized rubber material filling a 
spacing between the inner and outer sleeves 10, 12, to form the elastic 
body 14 whose inner and outer circumferential surfaces are secured to the 
inner and outer sleeves 10, 12, respectively. 
Between the inner and outer sleeves 10, 12 of the integral unit 16, there 
are disposed a plurality of rigid segments in the form of two 
semicylindrical metallic members 18, 18 each having a suitable thickness, 
such that the semicylindrical members 18, 18 are embedded in diametrically 
opposite portions of the elastic body 14, which are located on the 
opposite sides of the inner sleeve 10 as viewed in the load-receiving 
diametric direction in which the inner and outer sleeves 10, 12 are offset 
from each other. These semicylindrical members 18, 18 are opposed to each 
other in the above-indicated load-receiving diametric direction, such that 
the opposite circumferential end faces of one of the semicylindrical 
members 18 are spaced apart from the corresponding circumferential end 
faces of the other semicylindrical members 18 by a predetermined distance. 
As shown in FIG. 3, each semicylindrical member 18 extends along the 
corresponding one of the upper and lower halves of the inner 
circumferential surface of the outer sleeve 12. The semicylindrical 
members 18 have an axial length larger than that of the elastic body 14, 
so as to extend through the elastic body 14, as shown in FIG. 4. With the 
inner and outer circumferential surfaces of each semicylindrical member 18 
being secured by vulcanization to radially inner and outer portions 26, 28 
of the elastic body 14, the semicylindrical members 18, 18 are elastically 
connected to the inner and outer sleeves 10, 12 via the elastic body 14. 
As shown in FIG. 3, the elastic body 14 does not intervene between the 
circumferentially opposite end faces of one of the semicylindrical members 
18 and the corresponding end faces of the other cylindrical member 18. 
Thus, the two semicylindrical members 18 are opposed to each other with 
suitable clearances 20, 20 left between the corresponding circumferential 
end faces which face each other in the circumferential direction of the 
mount. More specifically, the elastic body 14 has a pair of inner voids 22 
formed in the radially inner portion 26, and a pair of outer voids 24 
formed in the radially outer portion 28, such that the corresponding 
circumferential end portions of the semicylindrical members 18 are 
radially interposed between and exposed to the inner and outer voids 22, 
24. The inner and outer voids 22, 24 are formed over respective given 
lengths in the circumferential direction of the elastic body 14, while 
extending over the entire axial length of the elastic body 14. These inner 
and outer voids 22, 24 serve to facilitate relative displacement of the 
semicylindrical members 18, 18 toward each other when the outer sleeve 12 
is radially inwardly compressed in a subsequent drawing process which will 
be described later. 
As is understood from the above description, the elastic body 14 is 
substantially divided by the semicylindrical members 18, 18 into the 
radially inner and outer portions 26, 28. Each of the semicylindrical 
members 18 has two holes 30, 30 formed through the thickness thereof, such 
that the holes 30 are spaced apart from each other in the circumferential 
direction of the member 18. The radially inner and outer portions 26, 28 
indicated above are connected to each other through these holes 30, 30 so 
as to provide the integrally formed elastic body 14. 
The elastic body 14 has an axial void 32 formed through one of the 
above-indicated diametrically opposite portions thereof at which the 
radial distance between the inner and outer sleeves 10, 12 is the 
shortest. The axial void 32 is formed through the entire axial length of 
the elastic body 14, and has a generally arcuate cross sectional shape as 
shown in FIG. 3, with a suitable circumferential length (about one-third 
of the circumference of the elastic body 14) along the inner 
circumferential surface of the upper semicylindrical member 18. The thus 
formed axial void 32 serves to reduce an amount of tensile strain in the 
elastic body 14 when the engine mount is installed in position such that 
the elastic body 14 is elastically deformed by the weight of the engine 
unit which acts on the engine mount so as to cause relative radial 
displacement of the inner and outer sleeves 10, 12, as described above. 
The thus constructed integral unit 16 of FIGS. 3 and 4 consisting of the 
inner and outer sleeves 10, 12, the semicylindrical members 18 and the 
elastic body 14 is radially inwardly compressed at the outer sleeve 12, by 
a suitable drawing operation using a circular array of eight dies, for 
example, whereby the present engine mount as shown in FIGS. 1 and 2 is 
obtained. 
When the integral unit 16 is radially inwardly compressed as described 
above, the compressive force applied to the outer sleeve 12 acts on the 
semicylindrical members 18, 18 through the radially outer portion 28 of 
the elastic body 14, so that the semicylindrical members 18, 18 are moved 
toward each other in the load-receiving direction in which the two members 
18, 18 are opposed to each other. In the instant embodiment, in 
particular, the inner and outer voids 22, 24 formed in the vicinity of the 
opposite circumferential ends of the semicylindrical members 18 permit the 
compressive force applied to the outer sleeve 12 to effectively act on the 
semicylindrical members 18, 18, for facilitating the relative displacement 
of the semicylindrical members 18, 18 toward each other. 
As the semicylindrical members 18, 18 are moved toward each other in the 
load-receiving direction, the diameter of the combination of the two 
semicylindrical members 18, 18 is substantially reduced, whereby an 
effective degree of the preliminary compression is given to the radially 
inner portion 26 of the elastic body 14 which is located radially inside 
of the semicylindrical members 18. 
As the compressive force is applied to the outer sleeve 12, the 
corresponding circumferential end faces of the semicylindrical members 18 
are brought into abutting contact with each other such that the plane 
including the mutually abutting circumferential end faces is perpendicular 
to the load-receiving direction. With a further compressive force applied 
to the integral unit 16, the corresponding circumferential end faces of 
the semicylindrical members 18 are pressed against each other, so that the 
semicylindrical members 18, 18 cooperate to constitute an integral 
cylindrical rigid split member in the form of a cylindrical metallic 
assembly 34 as shown in FIGS. 1 and 2. 
Once the semicylindrical members 18, 18 are formed into the cylindrical 
metallic assembly 34 in the manner as described above, the compressive 
force applied to the outer sleeve 12 no longer acts on the radially inner 
portion 26 of the elastic body 14. Consequently, a further increase in the 
compressive force applied to the outer sleeve 12 acts exclusively on the 
radially outer portion 28 of the elastic body 14, so that a suitable 
degree of preliminary compression is given to the radially outer portion 
28. 
By applying a suitable amount of compressive force to the outer sleeve 12 
of the integral unit 16 as described above, there is obtained an engine 
mount with a vibration damper according to the present invention, in which 
the cylindrical metallic assembly 34 disposed between the inner and outer 
sleeves 10, 12 is supported by the two sleeves 10, 12 through the elastic 
body 14. 
In the thus constructed engine mount, the elastic body 14 consisting of the 
radially inner and outer portions 26, 28 can be formed in only one 
vulcanization process. That is, the present engine mount is constituted by 
a single intermediate product in the form of the integral unit 16 which is 
prepared by only one vulcanizing operation for forming the elastic body 14 
secured to the inner and outer sleeves 10, 12 and the semicylindrical 
members 18. Thus, the present engine mount with a vibration damper has a 
considerably simple construction. 
Further, suitable degrees of preliminary radial compression can be given to 
both the radially inner and outer portions 26, 28 of the elastic body 14 
during the single drawing operation in which the compressive force is 
applied to the outer sleeve 12. Thus, the process of manufacturing the 
present engine mount is significantly simplified. Moreover, the 
cylindrical metallic assembly 34 is constituted by two or more rigid 
members formed by pressing of sheet members, rather than a pipe or other 
tubular member. Thus, the present engine mount can be manufactured with 
significantly improved efficiency, and the cost of manufacture of the 
mount is accordingly reduced. 
In the instant engine mount, the degree of the preliminary compression 
given to the radially inner portion 26 of the elastic body 14 can be 
suitably determined by adjusting the distance of movement of the 
semicylindrical members 18, 18 toward each other, that is, the dimension 
of the clearances 20 between the corresponding circumferential end faces 
of the semicylindrical members 18, 18 of the intermediate product 16. The 
degree of the preliminary compression given to the radially outer portion 
28 can also be suitably determined by adjusting the amount of the 
compressive force applied to the outer sleeve 12 after the two 
semicylindrical members 18 abut on each other. Thus, the degrees of the 
preliminary compression given to the radially inner and outer portions 26, 
28 of the elastic body 14 can be easily determined as desired, assuring a 
great degree of freedom in designing the engine mount. 
For instance, the integral unit 16 (intermediate product) as shown in FIG. 
3 is dimensioned such that the circumferential length of each clearance 20 
formed between the corresponding circumferential ends of the 
semicylindrical members 18, 18 is equal to 4.2 mm, and such that the 
outside diameter of the outer sleeve 12 before the drawing operation is 
equal to 100 mm. In the engine mount of FIG. 1 obtained from the thus 
dimensioned integral unit 16, the outside diameter of the outer sleeve 12 
is reduced by the drawing operation to 95 mm. In this case, the degree of 
the preliminary compression given to the radially inner portion 26 of the 
elastic body 14 is determined by the distance (i.e., 4.2 mm) of relative 
movement of the semicylindrical members 18, 18 toward each other. On the 
other hand, the degree of the preliminary compression given to the 
radially outer portion 28 of the elastic body 14 is determined by the 
amount of the compressive force which is applied to the outer sleeve 12 
after the semicylindrical members 18, 18 abut on each other and are formed 
integrally into the metallic assembly 34, based on the amount of reduction 
in the outside diameter of the outer sleeve 12 (100-95-4.2=0.8 mm). In 
this specific example, the preliminary compression is effectively applied 
to both the radially inner and outer portions 26, 28 of the elastic body 
14. 
While the present invention has been described in its presently preferred 
embodiment, for illustrative purposed only, it is to be understood that 
the invention is not limited to the details of the illustrated embodiment, 
but various changes, modifications and improvements may be made in the 
invention. 
For instance, the dimensions, configuration, weight and position of the 
cylindrical metallic assembly 34 as the cylindrical rigid split member may 
be suitably determined or changed as needed, depending on the required 
vibration damping and/or isolating characteristics of the mount. 
The axial void 32 formed through the elastic body 14 may be modified or 
eliminated, depending upon the required vibration damping and/or isolating 
characteristics of the mount. 
Further, the inner and outer voids 22, 24 formed in the vicinity of the 
opposite circumferential ends of the semicylindrical members 18, 18 are 
not essential to the practicing of the principle of the present invention. 
While the cylindrical metallic assembly 34 as the rigid split member is 
constituted by two rigid segments in the form of the two semicylindrical 
members 18, 18 in the illustrated embodiment, the rigid split member may 
be constituted by three or more arcuate segments or segments having other 
shapes, which are spaced from each other in the circumferential direction 
of the mount before the segments are brought into abutting contact with 
each other to form the generally cylindrical rigid split member. For 
instance, the rigid split member may have a polygonal shape such as a 
hexagon or octagon. 
Although the illustrated embodiment is adapted to be used as an engine 
mount for a motor vehicle, the concept of the invention may be embodied as 
vehicle body mounts, vehicle suspension bushings, and other elastic mounts 
whose applications are not limited to the motor vehicle. 
It is also to 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.