Abstrict Improvements are disclosed for a jaw crusher having converging
and opposed jaws defining a space for passage of material to be
crushed. An improved assembly for imparting oscillatory vibration
to at least one jaw comprises multiple eccentric means arranged
in vertically spaced apart relation and synchronously operated by
split drive means for producing more uniform and consistent operation
of the crusher under different load conditions. Another improvement
comprises at least two eccentric masses arranged in laterally spaced
apart relation on the one jaw by separate shafts which are independently
mounted by separate bearings whereby the size of both the eccentric
masses and bearings is proportionately reduced to permit crusher
operation at increased rates of rotation. A further improvement
comprises an elongated resilient member mounted on the frame structure
with a reaction member connected to the one jaw and surrounding
the elongated resilient member for permitting oscillatory movement
of the one jaw while limiting its travel in all directions on the
frame structure. Preferably, both jaws are similarly constructed
and mounted on the frame structure.
Claims What is claimed is:
1. An improved jaw crusher including a supporting frame structure,
a pair of opposed downwardly converging crusher jaws defining therebetween
a space for passage of material to be crushed, means supporting
one of the jaws in floating relation on the frame structure, means
supporting the other jaw on the frame structure for opposed crushing
action relative to the one jaw, and improved means for imparting
oscillatory vibration to the one jaw comprising
multiple eccentric means arranged in vertically spaced apart relation
on the one jaw for imparting oscillatory vibration to respective
portions of the jaw and producing more uniform and consistent operation
of the crusher under different load conditions, and
split drive means for synchronously operating the multiple eccentric
means,
each vertically spaced eccentric means comprising at least two
eccentric masses arranged on separate shafts in laterally spaced
apart relation, the separate shafts being independently mounted
on bearing means and interconnected by flexible coupling means,
the split drive means being coupled with the shafts for driving
the eccentric means in rotation.
2. The improved jaw crusher of claim 1 wherein the split drive
means is coupled with one shaft in each eccentric means.
3. The improved jaw crusher of claim 2 wherein the other jaw is
similarly supported as the one jaw and provided with similar multiple
eccentric means, the split drive means being coupled with the multiple
eccentric means on both jaws.
4. The improved jaw crusher of claim 1 wherein the means supporting
the one jaw comprises an elongated resilient member connected with
the frame structure behind the jaw, a reaction member connected
to the one jaw and surrounding the elongated resilient member for
permitting oscillatory movement of the jaw in response to the eccentric
means while at the same time limiting travel of the one jaw in all
directions on the frame structure.
5. The improved jaw crusher of claim 4 wherein the reaction member
is connected to a lower portion of the jaw and further comprising
additional resilient means mounted on the frame structure behind
an upper portion of the one jaw, releasable means connecting the
elongated resilient member with the frame structure and permitting
the elongated resilient member to be disconnected from the frame
structure to facilitate installation and removal of the jaw as a
unit.
6. The improved jaw crusher of claim 5 further comprising motor
means mounted on the frame structure and interconnected with the
eccentric means by the split drive means and releasable coupling
means allowing the eccentric means to be installed and removed as
part of the jaw unit.
7. An improved jaw crusher including a supporting frame structure,
a pair of opposed downwarding converging crusher jaws defining therebetween
a space for passage of material to be crushed, means supporting
one of the jaws in floating relation on the frame structure, means
supporting the other jaw on the frame structure for opposed crushing
action relative to the one jaw, and improved means for imparting
oscillatory vibration to the one jaw comprising
multiple sets of similar eccentric masses arranged in vertically
spaced apart relation, each set having at least two eccentric masses
arranged in laterally spaced apart relation on separate shafts independently
mounted on the one jaw by separate bearing means, the shafts for
each set of eccentric masses being interconnected by flexible coupling
means, and drive means operatively interconnected with the eccentric
masses for driving them in rotation and imparting oscillatory vibration
to the one jaw whereby the size of the eccentric masses is proportionately
reduced relative to a single eccentric mass for driving the one
jaw and the size of the bearings is similarly reduced permitting
operation of the eccentric masses at increased rates of rotation
as desired for achieving optimum operation of the crusher, one of
the shafts for each set of eccentric masses being interconnected
with the drive means by split gear means for synchronously operating
the multiple sets of eccentric masses.
8. The improved jaw crusher of claim 7 wherein the other jaw is
similarly supported as the one jaw and provided with similar laterally
spaced apart eccentric masses, the drive means being operatively
interconnected with the laterally spaced apart eccentric masses
on both jaws.
9. The improved jaw crusher of claim 8 wherein the means supporting
each jaw comprises an elongated resilient member connected with
the frame structure behind the jaw, a reaction member connected
to the jaw and surrounding the elongated resilient member for permitting
oscillatory movement of the jaw in response to the eccentric masses
while at the same time limiting travel of the jaw in all directions
on the frame structure.
10. The improved jaw crusher of claim 9 wherein the reaction member
is connected to a lower portion of the jaw and further comprising
additional resilient means mounted on the frame structure behind
an upper portion of the jaw, releasable means connecting the elongated
resilient member with the frame structure and permitting the elongated
resilient member to be disconnected from the frame structure to
facilitate installation and removal of the jaw as a unit.
11. The improved jaw crusher of claim 10 further comprising motor
means mounted on the frame structure and interconnected with the
eccentric masses by the split drive means and releasable coupling
means allowing the eccentric masses to be installed and removed
as part of the jaw unit.
12. The improved jaw crusher of claim 7 wherein the means supporting
the one jaw comprises an elongated resilient member connected with
the frame structure behind the one jaw, a reaction member connected
to the one jaw and surrounding the elongated resilient member for
permitting oscillatory movement of the one jaw in response to the
eccentric masses while at the same time limiting travel of the jaw
in all directions on the frame structure, the reaction member being
connected to a lower portion of the one jaw and further comprising
additional resilient means mounted on the frame structure behind
an upper portion of the one jaw, releasable means connecting the
elongated resilient member with the frame structure and permitting
the elongated resilient member to be disconnected from the frame
structure to facilitate installation and removal of the one jaw
as a unit.
13. The improved jaw crusher of claim 12 further comprising motor
means mounted on the frame structure and interconnected with the
eccentric masses by the split drive means and releasable coupling
means allowing the eccentric masses to be installed and removed
as part of the jaw unit.
14. In a jaw crusher including a supporting frame structure, a
pair of opposed downwardly converging crusher jaws defining therebetween
a space for passage of material, means supporting one of the jaws
in floating relation on the frame structure, means supporting the
other jaw on the frame structure for opposed crushing action relative
to the one jaw, an improved support for the one jaw comprising
an elongated resilient member connected with the frame structure
behind the jaw,
a reaction member connected to the jaw and cicumferentially surrounding
the elongated resilient member for permitting oscillatory movement
of the jaw in response to an eccentric means while at the same time
limiting travel of the jaw in all directions on the frame structure,
the reaction member being connected to a lower portion of the jaw
and further comprising additional resilient means mounted on the
frame structure behind an upper portion of the jaw,
releasable means connecting the elongated resilient member with
the frame structure and permitting the elongated resilient member
to be disconnected from the frame structure to facilitate installation
and removal of the jaw as a unit, and
motor means mounted on the frame structure and interconnected with
the eccentric means by releasable coupling means allowing the eccentric
means to be installed and removed as part of the jaw unit.
15. The improved jaw crusher of claim 14 wherein the other jaw
is similarly supported as the one jaw and provided with a similar
improved support.
16. The improved jaw crusher of claim 14 further comprising retainer
means mounted on the frame structure for preventing an upper end
of the one jaw from collapsing inwardly toward the other jaw particularly
when the upper end of the crusher is empty of material to be crushed,
the retainer means being further adapted to facilitate installation
and removal of the jaw as a unit.
Description FIELD OF THE INVENTION
The present invention relates to rock crushing machines and more
particularly to such machines wherein oscillatory vibration or motion
is produced in opposed jaws by means of eccentric masses or the
like.
BACKGROUND OF THE INVENTION
U.S. Pat. No. 3079096 entitled "Crushing Apparatus"
issued Feb. 26 1963 to David P. McConnell, father of the inventor
herein. The crusher described and claimed in that patent is particularly
representative of the prior art with respect to the present invention
and is accordingly discussed in greater detail below. The jaw crusher
of the present invention includes certain features in common with
the apparatus of the above patent and also in common with a copending
U.S. patent application, Ser. No. 06/943548; filed Dec. 18 1986
and entitled "Improved Jaw Crusher with Drop-In Jaw" invented
by Laurence U. Turly and David P. McConnell, also the inventor herein.
Accordingly, both U.S. Pat. No. 3079096 and the copending application
referred to above are incorporated herein as though set forth in
their entirety in order to provide a more complete understanding
of the present invention, particularly as to common crushing apparatus
features.
The crushing apparatus of the present invention also includes certain
features in common with apparatus disclosed in another copending
U.S. patent application, Ser. No. 06/823309; filed Jan. 28 1986
by David P. McConnell, the inventor herein, entitled "Jaw Crushing
Apparatus" and now assigned to the assignee of the present
invention. Accordingly, that copending and commonly owned reference
is also incorporated herein as though set forth in its entirety.
Referring now to the incorporated references, U.S. Pat. No. 3079096
disclosed a jaw crusher of the type generally referred to above
wherein an eccentric mass was supported for rotation behind each
of its opposed jaws. Substantial forces acting upon the jaws were
absorbed by resilient means including wheels with pneumatic tires
arranged in shoes or cylindrical tracks partially surrounding the
tires. In addition to absorbing tremendous shock loading on the
jaws, the resilient tires permitted the jaws to move away from each
other as necessary when uncrushable material formed, for example,
from hardened steel or the like, entered between the jaws.
Accordingly, the jaw crusher of the reference was particularly
effective in crushing materials such as rock while preventing the
jaws or other portions of the crusher from being damaged by uncrushable
material passing between the jaws.
Other jaw crushers including vibratory jaw crushers with opposed
jaws operated by rotating eccentric masses have also been disclosed
in the prior art. For example, reference is made to U.S. Pat. No.
1247701 issued Nov. 27 1917 to Michaelsen. However, at least
for purposes of the present invention, these other prior art jaw
crushers are believed to be generally equivalent to that of the
above incorporated reference.
Although the prior art jaw crushers discussed above were very effective
for their purpose, it has been found desirable to further improve
their design for further enhancing jaw crusher operation in a variety
of applications. Particularly in connection with large size crushers
adapted for crushing large rocks or the like, some difficulty has
been found in assuring uniform transmission of oscillatory motion
to different parts of the jaws. For example, when large rocks are
the like which are difficult to crush are trapped between certain
portions of the opposed jaws, vibratory forces applied to the jaws
follow the path of least resistance so that the jaws tend to experience
increased vibratory movement at a location away from the large rock.
This tendency naturally interferes with rapid and efficient crusher
operation.
In addition, difficulty has also been encountered in assuring uniform
transmission of vibratory motion to jaws of increased size. This
is true both for jaws of extended or increased lateral dimension,
for example, to achieve increased throat size, or increased longitudinal
dimension, for example where a longer, more gradual nip is desired
between the jaws.
It has also been noted that, particularly with larger crushers,
assembly and disassembly is made more difficult. This is most noticeable
in connection with the jaws themselves which tend to experience
concentrated wear during operation of the crusher.
Accordingly, there has been found to remain a need for a jaw crusher
exhibiting improvements in the areas discussed above as well as
in other areas.
SUMMARY OF THE INVENTION
It is therefore an object of the present invention to provide an
improved jaw crusher capable of overcoming one or more of the disadvantages
discussed above.
It is a further object of the invention to provide a jaw crusher
having opposed jaws with at least one of the jaws being supported
in floating relation on a supporting frame structure, improved means
for imparting oscillatory vibration to the one jaw comprising multiple
eccentric means arranged in vertically spaced apart relation on
the one jaw in order to impart oscillatory vibration to respective
portions of the one jaw for producing more uniform and consistent
operation of the crusher under different load conditions, split
drive means synchronously operating the multiple eccentric means.
It is a further object of the invention to provide such a crusher
with opposed jaws wherein at least two eccentric masses are arranged
on separate shafts in laterally spaced apart relation, the separate
shafts being independently mounted on bearing means and interconnected
by flexible coupling means.
The two arrangements referred to above can of course be incorporated
in a single jaw crusher wherein vertically spaced apart eccentric
means each comprise at least two eccentric masses arranged on separate
shafts independently attached to the jaw by bearing means. In a
crusher including either or both laterally spaced eccentric masses
and/or vertically spaced eccentric masses, it has been found that
vibratory motion can be more effectively and uniformly introduced
into different portions of the jaw, particularly where the jaws
are of relatively large size. At the same time, with the size of
the eccentric masses being proportionately reduced relative to a
single eccentric mass for driving the jaw, the size of the bearings
supporting the multiple eccentric masses is similarly reduced. Since
the size of the bearings tends to limit the rate of rotation possible
for the eccentric masses, it is immediately apparent that the arrangements
contemplated by the present invention are capable of permitting
operation at increased rates of speed as may be desired for achieving
optimum pressure operation.
It is yet another object of the invention to provide such a jaw
crusher for facilitating installation and removal of either or both
jaws wherein the jaw is formed with a reaction member either integrally
formed with the jaw or connected thereto, the reaction member surrounding
an elongated resilient member attached to the supporting frame structure.
With this arrangement, the single elongated resilient member serves
to permit oscillatory movement of the jaw in response to the eccentric
means while at the same time limiting travel of the jaw in all directions
on the frame structure. This arrangement is also particularly advantageous
in avoiding multiple restraints for the jaw which tend to work against
each other, for example, and absorb part of the vibratory force
developed by the rotating eccentric means. Thus, with such a design,
a greater portion of the vibratory force can be transferred through
the jaw faces to the material to be crushed for increased efficiency.
In a preferred design, the reaction member surrounding the elongated
resilient member is preferably attached to a lower portion of the
jaw with additional resilient means being mounted on the frame structure
behind an upper portion of the jaw. As will be disclosed in greater
detail below, such an arrangement particularly facilitates installation
and removal of the jaw as a unit from the crusher.
Additional objects and advantages of the invention are made apparent
in the following description having reference to the accompanying
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side view, with parts removed and other parts shown
in cross section, to more clearly illustrate the construction of
a jaw crusher according to the present invention.
FIG. 2 is a plan view of the crusher taken generally from the top
of FIG. 1 the jaw crusher of FIG. 2 including a base structure
and drive assembly which are omitted in FIG. 1 for greater clarity.
FIG. 3 is an end view of the crusher taken generally from the right
side of FIG. 1.
FIG. 4 is a fragmentary side view of the opposed jaws in the crusher
to better illustrate their unitary construction and configuration,
one of the opposed jaws being illustrated with resilient means for
limiting oscillatory movement of the jaw.
FIG. 5 is a further view of one of the jaws, taken for example
from the right side of FIG. 4 with the resilient means being removed.
DESCRIPTION OF THE PREFERRED EMBODIMENT
A jaw crusher constructed according to the present invention is
generally indicated at 10 in the drawings and includes a base frame
assembly 12 and a fabricated floating frame structure or jaw carriage
frame 14. The base frame assembly 12 includes a platform 16 with
upright frame members 18 and 20. Both the base frame assembly 12
and jaw carriage frame 14 are substantially reinforced as illustrated.
The jaw carriage frame 14 includes opposed upright side plates
24 and 26 which are rigidly interconnected by cross members 28.
The jaw carriage frame or floating frame assembly 14 is resiliently
supported upon the base frame 12 by a plurality of coiled springs
30 interposed between the upright frame members 18 and 20 of the
base frame 12 and the cross members 28 of the floating frame assembly
14. The springs 30 are positioned relative to both the upright frame
members 18 and 20 and the cross members 28 by means of positioning
cups 32.
A pair of pressure jaws 34 and 36 are mounted on the jaw carriage
frame 14 in a manner described in greater detail below for allowing
oscillatory or vibratory movement of the jaws in synchronized relation
with each other. The mounting of the jaws 34 and 36 upon the floating
frame assembly 14 is of particular importance because of the very
substantial shock forces acting upon the jaws during operation of
the crusher.
In any event, it will be more apparent from the following description
that, in their oscillatory or vibratory movement, the jaws experience
an upward stroke where they move upwardly and away from each other
followed by a downward stroke where the jaws move downwardly and
toward each other. The upward and downward strokes of the jaws produce
vibratory and oscillatory movement in order to develop crushing
force on rocks or other material passing between the jaws.
As noted above, the crusher jaws 34 and 36 are of substantially
similar construction and are formed as mirror images to each other.
Accordingly, the following description for the crusher jaw 34 also
applies to the crusher jaw 36 with similar primed numerical labels
being employed. However, it is to be noted that one of the jaws,
for example that indicated at 36 could be relatively fixed upon
the jaw carriage frame 14 with oscillatory or vibratory movement
between the jaws being produced by movement of the one jaw 34 by
itself. In any event, similar operation of both jaws is generally
preferred in order to achieve greater crushing forces.
The jaw crusher 10 as described above generally conforms with at
least one embodiment in the copending references. Similar numerical
labels have also been employed to further facilitate comparison.
However, it is to be noted that there are otherwise substantial
differences in the manner in which the jaws and other portions of
the crusher are constructed and supported for enhancing crusher
operation.
Referring now particularly to FIGS. 1 and 4 the crusher jaws 34
and 36 are formed with upper hardened face plates 38 and 38' and
lower hardened face plates 42 and 42' respectively. The lower face
plates are substantially shorter in vertical dimension that the
upper face plates. Although not a particular feature in connection
with the present invention, it is noted that the upper and lower
plates are preferably formed from very hard metal and secured to
a backing plate 40 or 40' by means of countersunk bolts or studs
(not shown) in order to facilitate removal or replacement of the
facing portions of the jaws which are particularly susceptible to
wear.
Referring to the unitary jaws as illustrated in FIGS. 1 and 4
the angular relationship between the upper and lower face plates
38 42 and 38', 42' is of particular importance within the present
invention in order to achieve more effective crushing action on
rock or other material passing between the jaws. Generally, it is
desirable for the lower face plates 42 and 42' to be substantially
parallel with each other, for example, when fine crushing is desired
within the apparatus 10. At the same time, it has been found desirable
to form a converging angle between the upper face plates 38 and
38' for a number of reasons discussed at greater length in the incorporated
copending reference noted above.
In any event, it is to be kept in mind in connection with the present
invention that the multiple drive means provided by the present
invention facilitates not only construction of jaws having greater
lateral dimensions but also jaws having greater vertical dimensions.
The greater vertical dimensions for the jaws permit, for example,
formation of a longer tapered throat between the upper face plates
of the two jaws.
Within a jaw crusher as described above, there are three particular
areas of construction which are of importance in connection with
the present invention. These three features include (1) novel upper
and lower resilient elements 46 and 48 for positioning the jaw 34
(2) a multiple eccentric drive assembly generally indicated at 44
in FIG. 5 and (3) construction of the jaws 34 and 36 and associated
elements of the crusher as described in greater detail below for
facilitating assembly and disassembly of the jaws 34 and 36 in unitary
fashion from the crusher 10. These elements are described in greater
detail below.
Initially, the upper and lower elongated resilient elements 46
and 48 allow response of the jaws to the rotating eccentric masses
for producing the desired oscillatory movement of the jaws. In addition,
the resilient elements 46 and 48 limit travel of the jaws in a manner
described in greater detail below.
The upper elongated resilient element 46 is formed by multiple
members or tires 50 which are both resilient and compressible. The
tires 50 are mounted on a single shaft or axle 52 which is supported
at its opposite ends by bearing mounts 54 and 56 which are adjustable
on the jaw carriage frame 14 for varying the distance or throat
formed between the jaws 34 and 36.
The lower elongated resilient element 48 is similarly formed by
tires 58 mounted on a single shaft or axle 60 which is supported
at its opposite ends by bearing mounts or pillow blocks 62 and 64.
The pillow blocks 62 and 64 are similarly adjustable on a lower
portion of the jaw carriage frame 14 while also being detachable
from the frame 14 in order to facilitate assembly and disassembly
of the jaw 34 from the crusher 10 in unitary fashion as described
in greater detail below.
The jaw 34 is formed with a reaction member 66 in the form of a
rigid shoe or cylindrical track which entirely surrounds the tires
58. In this manner, the reaction member 66 serves to interact with
the tires 58 for limiting travel of the jaw 34 in all directions
during operation of the crusher. Because of the construction of
the reaction member 66 the upper tires 50 act directly against
the jaw itself since they do not serve a function of limiting the
stroke or travel of the jaw.
Thus, the construction of the jaw is unitary to facilitate its
being installed or removed from the crusher. At the same time, since
travel of the jaw in all directions is limited only by the reaction
member 66 the design of the jaw further avoids interference which
might occur if a further reaction member (not shown or employed
in the invention) were necessary. Such an arrangement of upper and
lower reaction members is illustrated in the copending reference.
By comparison, the design of the present jaw avoids interference
between such members which might tend to absorb or neutralize a
portion of the oscillatory or vibratory force otherwise being transferred
to the jaw faces.
Before completing the description of the unitary jaw and the manner
in which it can be assembled or disassembled from the crusher, the
construction of the multiple eccentric drive assembly 44 is first
described. Referring particularly to FIG. 5 each jaw, particularly
that indicated at 34 is provided with multiple sets of eccentric
means generally indicated at 68 and 70. The eccentric means 68 and
70 which are vertically spaced apart upon the jaw 34 each include
laterally arranged eccentric masses 68A, 68B and 70A, 70B so that
four uniformly sized eccentric masses are arranged both laterally
and vertically upon the jaw 34 to facilitate more uniform transmission
of oscillatory motion to all portions of the jaw.
Furthermore, the upper eccentric masses 68A and 68B are arranged
on separate shafts 72 and 74 which are interconnected by a flexible
drive coupling 76 while being independently coupled with the jaw
34 through separate bearing mounts 72A, 72B and 74A, 74B. The lower
eccentric masses 70A and 70B are similarly mounted on separate shafts
78 and 80 which are also interconnected by means of a flexible drive
coupling 82 and supported upon the jaw 34 by independent bearing
mounts 78A, 78B and 80A, 80B.
In addition to being laterally and vertically arranged upon the
jaw for more uniform transmission of force to the jaw, this arrangement
permits a number of advantages in the invention. Initially, with
the laterally spaced eccentric masses being arranged on separate
shafts, there is no problem of maintaining alignment between the
two eccentric masses. Also, with the four eccentric masses 68A,
68B and 70A, 70B replacing a single eccentric mass, the independent
bearings for the various eccentric masses can be of substantially
reduced size and diameter. This in turn permits operation of the
eccentric masses at higher rates of rotation, at least partly because
of the reduced mass in the bearings. Still further, the reduced
size of the eccentric masses permits them to be arranged closer
to the face 38 of the jaw so that oscillatory motion is more effectively
transferred to the jaw face at least partly because of the reduced
moment arm between the jaw face and the eccentric masses.
Each of the flexible drive couplings 76 and 82 is of generally
conventional construction for coupling the respective shafts 72
74 and 78 80 while allowing them to be independently supported
by their respective bearings. For example, referring particularly
to FIG. 5 the flexible drive couplings 76 and 82 are each formed
by members 84 and 86 which are respectively coupled with the shaft
72 and 74 or 78 and 80 while being coupled for rotation with each
other by means of an internal spider 88.
Referring also to FIGS. 2 and 3 all of the eccentric masses for
both jaws 34 and 36 are operated by a single drive motor 90 which
is coupled with both the upper and lower eccentric means 68 and
70 by a split drive train generally indicated at 92. The motor 90
is connected with the split drive train 92 through drive belts generally
indicated at 94. The split drive train 92 itself comprises drive
gears 96 98 100 and 102 which are interconnected respectively
with the upper and lower eccentric means for each of the jaws 34
and 36.
Referring particularly to FIG. 3 the respective drive gears are
interconnected with the upper and lower eccentric means 68 70 and
68', 70' for the jaws 34 and 36 by means of universal couplings
all indicated at 104. The universal couplings 104 further avoid
possibilities of misalignment while also providing means for uncoupling
the eccentric means from the drive train to facilitate removal and
installation of the jaws in unitary fashion.
Referring again to the construction of the upper and lower elongated
resilient elements 46 and 48 the pillow blocks 62 and 64 can be
simply disconnected from the jaw carriage frame 14 to permit the
lower tires 58 and shaft 60 to remain within the reaction member
66 so that they form part of the unitary jaw during assembly and
disassembly. Furthermore, with the pillow blocks 62 and 64 being
disconnected, the lower end of the jaw 34 as viewed for example
in FIG. 1 can be shifted outwardly or to the right so that the
upper end of the jaw 34 drops out of engagement with the upper elongated
resilient element 46. Thereafter, the entire unitary jaw 34 can
simply be moved away from the crusher 10 for repairs or replacement
as desired. Similarly, the unitary construction of the jaw 36 permits
it to be assembled or disassembled from the crusher 10 in the same
manner.
In addition to facilitating removal and installation of the jaws
34 and 36 these features of the crusher 10 also permit the overall
height of the crusher 10 to be reduced not only to minimize the
need for head room but also to lower the center of gravity for the
crusher. The need for available overhead space is further reduced
because of the ability to remove and install the unitary jaws 34
and 36 in the manner described above. Still further, in addition
to reducing the overall height of the crusher 10 the throat area
106 formed between the jaws 34 and 36 and by the lateral liners
108 and 110 mounted on the jaw carriage frame 14 to extend further
downwardly so that they terminate closely adjacent a hopper or other
container 112 for receiving crushed rock or other material from
the crusher. The generation of dust can be further reduced by arranging
a shroud 114 around the lower end of the throat area 106 so that
the shroud 114 extends downwardly toward the hopper 112.
Accordingly, there has been disclosed a novel and improved jaw
crusher offering a number of advantages as described in detail above.
Numerous modifications and variations are possible in addition to
those specifically described above. Accordingly, the scope of the
present invention is defined only by the following appended claims.
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