Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
l~S7~8
1 This invention relates generally to rock crushing
apparatus and more particularly to an improved gyratory or
cone crusher.
~ critical area in the operation of gyratory crushers
is the system employed to permit adjustment of the bowl
assembly relative the gyrating crusher head and mantle. In
view of the significant size and weight of the structure in-
volved, many existing crushers of this type have utilized a
large number of peripherally disposed bolts, each provided
with suitable lock nuts which must be individually manipulated
whenever it is desired to alter the adjustment of the bowl
assembly to vary the product size. Even then, additional means
must be used in order to break loose the rigid connection
between the bowl assembly, its annular support ring and the
lS upper portion of the crusher frame before any adjustment of
the bowl assembly may be made. Additionally, structure should
be provided in the form of shock absorbing means designed to
serve as a load relief to protect the bowl liner, mantle and
associated structure of the gyrating mantle should tramp iron
or other non-crushable material be introduced between the liner
and mantle.
By the present invention an improved structure is
provided to facilitate the adjustment and clamping of the bowl
assembly as well as to break loose the clamping assembly prior
to any subsequent adjustment. Cooperating with the means
supporting the b~wl assembly upon the crusher frame are a
plurality of hydraulic load relief cylinders, each of which
i8 provided with a fluid accumulator to regulate the actuation
of the cylinders. All of the aforementioned structure is con-
trolled by a plurality of hydraulic systems which are connected
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1 in series and are directly related to one another whereby
a uni~ue cooperation is achieved to provide a practically
r ;,~ b~l
A automatic adjustment of the ~ liner with the only manual
operation involved being the addition of or removal of one or
more shims at each of three bowl support flanges radially ex-
tending from the bowl assembly at egui-distant points over-
lying a bowl support ring.
Cooperating with the above referenced structure is
an improved anti-spin assembly connecting between the base of
the crusher frame and the top of the crusher head and which is
likewise regulated by means of a fluid system to inhibit un-
desirable rotation of the crusher head relativeAthe bowl liner
during the absence of any feed material between the bowl liner
and mantle.
Accordingly, one of the primary objects of the present
invention is to provide a gyratory crusher having an improved
means for adjustably positioning the bowl assembly relative
the crusher head by means of a plurality of removable shims
which are automatically clamped and released by means of hydrau-
lically operable elements.
Another object of the present invention is to pro-
vide a gyratory crusher including improved bolt means for
retaining the crusher bowl support ring in locking engagement
with a segmented bowl clamp ring in order to retain the bowl
assembly in its adjusted position and which i8 regulated by
means of hydraulically operable elements.
Still another object of the present invention is to
provide a gyratory crusher having an improved system for
breaXing loose the wedge clamping fit between a bowl clamp
ring and bowl ~upport ring by means of a plurality of lift
1~?577~8
1 cylinders between the bowl assembly and bowl clamp ring,
which cylinders are hydraulically actuated.
A further object of the present invention is to pro-
vide a gyratory crusher having a plurality of load relief
cylinders peripherally disposed about the frame of the crusher
and joining the bowl support ring and upper support surface
of the frame with each relief cylinder hydraulically connected
to an individual fluid accumulator and at the same time hydrau-
lically connected in series with each adjacent relief cylinder
and a pressure regulated source of fluid.
With these and other objects in view which will be
more readily apparent as the nature of the invention is better
understood, the invention consists in the novel construction,
combination and arrangement of parts hereinafter more fully
described, illustrated and claimed.
A preferred and practical embodiment of the invention
is illustrated in the accompanying drawings in which:
FIGURE 1 is a top plan view of the improved gyratory
crusher of the present invention and most clearly illustrates
the hydraulic aspect of the apparatus.
FIGURE 2 is a vertical sectional view taken along the
line 2-2 of FIG. 1.
FIGURE 3 is a side elevation of the present invention
taken along the line 3-3 of FIG. 2.
FIGURE 4 is an enlarged vertical sectional view taken
along the line 4-4 of FIG. 2 more clearly illustrating the
anti-spin structure of the present invention.
FIGURE 5 is a bottom plan view taken along the line
5-5 of FIG. 4.
PIGURE 6 is an enlarged side elevation illustrating
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the bowl retainer bracket and adjustment shims associated there-
with.
FIGURE 7 is a vertical sectional view taken along the
line 7-7 of FIG. 6.
FIGURE 8 which is on the same sheet as FIGURE 3, is
a vertical sectional view, greatly enlarged, and illustrates a
plurality of the guide pins carried by the bowl support ring in
the various relative positions they would appear were a piece
of non-crushable material to be caught within the crusher.
FIGURE 9 which is on the same sheet as FIGURE 1, is
a fragmentary vertical sectional view illustrating one of the
hydraulic lift cylinder assemblies.
Similar reference characters designate corresponding
parts throughout the several figures of the drawings.
Referring now to the drawings, particularly FIGS.
1-3, the present invention will be seen to comprise a gyratory
crusner including a peripheral frame 1 having disposed there-
within a crushing mantle 2 adapted to cpoperate with a relatively
stationary liner 3 carried by a normally stationary bowl assembly
generally designated 4, and which is mounted atop the peripheral
frame 1. As shown most clearly in FIG. 2 of the drawings, the
conical mantle 2 is removably attached to a conical crusher head,
generally designated 5, by means of a mantle bolt 6 which co-
operates with a mantle nut 7, which fastener assembly is pro-
tected by means of a removable mantle cap 8. The crusher head
5 is supported upon an eccentric, generally designated 9, by
means of a plurality of upper thrust bearings 10 and upperouter
radial bearings 11. The eccentric in turn is supported upon
the base frame 12 by means of lower thrust bearings 13 and
retained for rotary movement by means of a fixed vertical bearing
shaft 14, the upper portion of
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which radially supports the eccentric by means of upper in-
terior radial bearings 15 and lower radial bearings 16.
Gyratory motion is imparted to the crusher head and
its mantle by means of a drive shaft assembly, generally des-
ignated 17, which contains a drive shaft 18 disposed within
the drive housing 19 and provided with a drive pinion 20
constantly meshing with the ring gear 21 affixed to the lower
portion of the eccentric intermediate the lower thrust bearings
13 and lower radial bearings 16. The aforementioned bowl
assembly 4 includes a cylindrical body 22 containing suitable
attaching means 23 for rigidly connecting the bowl liner 3
thereto with its upper portion adjacent a feed opening 24 within
the feed hopper 25 mounted atop the cylindrical body 22. The
outer periphery 26 of the bowl assembly cylindrical body 22 is
provided with a plurality of radially extending bowl adjustment
flanges 27 extending from the upper plane of the cylindrical
body 22 and adapted to cooperate with a corresponding number
of bawl retainer brackets 28 in a manner to be described here-
inafter.
Also extending radially from the outer periphery 26
of the cylindrical body of the bowl assembly are a corresponding
number of lift cylinder assemblies, generally designated 29,
and shown in FIGS. 3 and 9. Preferably there are three lift
cylinder assemblies 29 and three bawl adjustment flanges 27
equi-spaced about the periphery of the bowl assembly. ~he
most efficient operation of the invention has been found when
utilizing three bawl retainer brackets 28 and three lift cylinder
assemblies 29 and accordingly it will be understood that each
one of these elements will be disposed 120 from the remaining
two similar elements.
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i~S~7~8
To support the entire bowl assembly 4, the upper
portion of the peripheral frame 1 is formed with an inverted
V-way 104 comprising a pair of upwardly and inwardly inclined
or tapered support surfaces 30-30 extending in a circular
manner about the apparatus frame and each of which describes
a circumference the diameter of which is substantially greater
than that of the bowl assembly outer periphery 26. Overlying
the frame inverted V-way 104 is an annular bowl support ring,
generally designated 31, having a top surface 32 extending in-
wardly to describe circular inner periphery 33 forming a close
sliding fit with the outer periphery 26 of the bowl assembly
cylindrical body 22. ~he undersurface of the bowl support
ring 31 adjacent the bowl assembly is provided with a bowl
wedge surface 34 which is inclined downwardly and outwardly
from a point spaced well outwardly from the inner periphery 33
and also includes a pair of female tapered surfaces 35-35
forming a downwardly facing cavity 36, the cross section of which
is frusto-conical and is adapted to mate with the similarly
tapered male support surfaces 30-30 of the frame V-way 104.
The afore-mentioned bowl support ring wedge surface
34 cooperates with a segmented bowl clamp ring 37 which is
substantially triangular in cross sectional configuration and
includes a bowl wedge surface 38 mating with the bowl support
ring wedge surface 34 while its inner periphery 3g engages the
outer periphery 26 of the cylindrical body 22 as shown most
clearly in the left hand portion of FIG. 2 of the drawings.
Prior to operation of the instant crusher apparatus,
the bawl assembly 4 must be initially vertically oriented within
the confines of the inner periphery 33 of the bowl support
ring 31 at the proper elevation to locate the bowl liner 3 in
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a spaced relationship to the crusher mantle 2 so that the de-
sired product size will be achieved during operation of the
apparatus. Inasmuch as the bowl support ring 31, which is an
integral circular member, will be fixedly supported upon the
5 upper portion of the peripheral frame 1 during normal operation
of the crusher it will follow that means must be provided to
interlock the bowl assembly 4 and the bowl support ring 31 in
various selected positions of vertical relationship. From a
review of FIG. 2 of the drawings, it will be seen that before
10 the locking and adjusting means are actuated the bowl assembly
4 is free to be vertically displaced a substantial distance
with the bawl adjustment flanges 27 moving within the con-
fines of the bowl retainer brackets 28.
The details of the brackets 28 are shown more clearly
15 in FIGS. 3, 6 and 7 of the drawings, wherein it will be seen
that a plurality of the brackets 28, preferably three, are
equi-spaced about the periphery of the bowl assembly and each
bracket comprises a cross-head 40 having a pair of depending
side walls 41-41 each having a laterally extending foot 42
20 disposed upon the top surface 32 of the bowl support ring 31
and suitably secured thereto such as by means of the attaching
lts 43. During the initial assembly of the apparatus, the
~wl assembly 4 is lowered into position with each of the bowl
adjustment flanges 27 disposed above the support ring top
25 surface 32 and thereafter the plurality of retainer brackets
28 are dropped over the flanges 27 and the bolts 43 installed
so that the bawl assembly will thereafter be limited to verti-
cal displacement as defined by the limits of the opening 44
within the brackets 28. A shim stud 45 extends through each
30 bracket cro~s-head 40 down through the opening 44 and is secured
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1 to a base plate 45' disposed above the upper portion 32 of
the support ring 31 and i8 provided with a hydraulic washer,
generally designated 46, on the upper portion of its shank
immediately above the top of the cross-head 40. Suitable ad-
justable limit means such as the nuts 47' are carried by theuppermost distal portion of the shim stud 45. Hydraulic washers
as such are well known in the art and the example as shown in
the drawings attached hereto includes a cylinder unit 47 and
a vertically displaceable piston unit 48. The specific oper-
ation of the hydraulic washers 46 will be described hereinafter.
When the bowl assembly 4 has been lowered to the properelevation according to the desired crusher product size one
or more shims are inserted between the bottom surface 49 of
the cross-head 40 and top surface 50 of the bowl flange 27
as well as between the bottom surface 51 of the flange and the
top surface of the stud base plate 45' resting upon the support
ring 31 so as to occupy all free space within the bracket
opening 44 both above and below the bowl flange 27 as shown in
FIGS. 2 and 7. The upper shims 52 and lower shims 53 are
preferably of the same construction although, of course, various
thicknesses may be employed and each includes a central longi-
tudinal slot 54 through one end thereof adapted to straddle
the shank of the shim stud 45, as well as a separate enclosed
opening 55 adjacent the outer edge for the reception of a
guide key 56, which key will be seen to extend through all of
the stacked openings of both the upper and lower shims 52 and
53 respectively. In order to prevent the key 56 and all of
the upper and lower shims from shifting from the fully inserted
po~ition as sh~n in FIG. 7 before the shim stud 45 is clamped
or locked, a p~ir of hooks 57 extend outwardly from either side
l~S77~t~
of each bowl adjustment flange 27 to overlie the outer face of
the guide key 56.
When the bawl assembly has thus been vertically
positioned and the proper sizes and numbers of shims have
5 been inserted both above and below the bawl adjustment flange
27 to fill all free space within the opening 44, each of the
associated hydraulic washers 46 are actuated, as will be
described hereinafter, to extend the piston unit 48 upwardly
against the stationary nuts 47' and urge the cylinder unit 47
10 dawnwardly agair~t the bracket 28 whereby a positive up~ard
force is applied to the stud 45 and the base plate 45' attached
to the lower distal portion so that the shims 52 and 53 and
the sandwiched bowl flange are tightly clamped with respect
to the surrounding bracket and thus also relative to the bowl
15 support ring 31 inasmuch as each bracket is bolted to the
support ring.
It will be understood that the above-described
selection and installation of the shims 52 and 53 merely serve
the purpose of properly locating the bawl liner 3 at the
20 desired elevation relative to the crusher mantle 2 according
to the desired product size by positioning the bowl assembly
relative its surrounding support ring 31 and thus it is
necessary to thereafter employ more positive and stronger
clamping means to rigidly retain the entire periphery of the
25 b~wl assembly 4 at this elevation relative to the top of the
peripheral frame 1.
Quite obviously the shims could never withstand the
tremendous shock generated by the pounding of stone within the
cru~hing zone and accordingly a segmented bowl clamp ring 37
30 i~ utilized in combination with the outer periphery 26 of the
7~
1 bowl assembly cylindrical body 22 and the bowl support ring
31 in order to rigidly clamp the entire periphery of the bowl
assembly to the normally stationary bowl support ring. The
clamp ring 37 actually comprises six separate arcuate segments
substantially describing an arc of 60 each and wherein the
arcuate configuration of the inner surace 39 thereof is con-
gruent with the outer periphery 26 of the bowl assembly cylin-
drical body while the bowl clamp ring wedge surface 38 is like-
wise contruent with the bowl support ring wedge surface 34
so that vertical displacement of each clamp ring segment 37
will provide an ever tightening or clamping action resulting
in an interlocking of the bowl assembly and bowl support ring
by means of the clamp ring 37.
The above mentioned clamping action is achieved by
means of a plurality of clamp ring bolts 58, preferably two
such bolts serving each one of the ring segments 37. Each
bolt 58 includes an upper portion 59 disposed well above the
top surface 32 of the bcwl support ring 31 and a shank portion
60 extending downwardly through the bowl support ring and
bowl clamp ring 37 and terminating in a head 61 engaging the
bottom surface 62 of the clamp ring. The clamp ring bolts 58
are provided with hydraulic washers 46' of a construction
similar to the hydraulic washers 46 heretobefore described, and
which engage the top surface 32 of the bowl support ring 31
on the one hand and are retained about the bolt uppex portions
59 by means of a plurality of adjustment nuts 63 engaging the
threaded area of the upper portions 59. It will now be apparent
that upon the application of hydraulic fluid to the hydraulic
washerfi 46', the piston units 48 and cylinder units 47 will
be expanded relative to one another whereby an upward force
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i' ''~7~8
is applied to the undersurface of the nuts 63 and a simultan-
eous downward force directed upon the top surface 32 of the
bcwl support ring 31 so that the segmented bowl clamp rings 37
will be drawn upwardly to provide a positive wedging or clamping
5 action rigidly interlocking the entire periphery of the bowl
assembly 4 relative to the bowl support ring 31.
The hydraulic washers 46 and 46' are of the single
action type; that is, fluid pressure is applied through a
single fitting in order to expand relatively the piston and
10 cylinder units thereof and when this fluid pressure is relieved
the expansion force is terminated and an outside force must
be applied in order to collapse the piston relative to the
cylinder. Keeping the foregoing in mind it will be appreciated
that in order to subsequently readjust the elevation of the
15 bowl assembly 4 it is necessary to break loose the clamping
or wedging action of the bowl clamp rings 37 before it is
possible to readjust the bawl assembly since the mere relaxation
of positive fluid pressure to the hydraulic washers 46' will
not cause the bowl clamp ring segments 37 to drop from their
20 elevated clamping relationship with the outer periphery 26 of
the bawl assembly and the wedge surface 38 of the bowl support
ring 31. q~his breaking action of the wedged clamp ring 37 is
achieved by means of a single lift cylinder assembly 29 associ-
ated with each pair of segments of the bowl clamp ring 37 as
25 shown most clearly in FIG. 9 of the drawings.
Each lift cylinder assembly 29 comprises a cylinder
unit 64 fixedly attached to a bowl lift flange 65 and extend-
ing downwardly therethrough to a point adjacent the top surface
32 of 'che ba~l support ring 31. A vertical aperture 66 is
30 provided through the ba"l support ring beneath the cylinder unit
--11--
1~57~
1 64 for the reception of a clamp release pin 67 which is actu-
ally an extension of a piston within the cylinder unit 64 and
wnich extends downwardly through the aperture 66 to engage a
horizontal platform 68 forming the bottom of a cut-out 69 pro-
vided in the bowl clamp ring 37. It will now be appreciated
that upon the application of a positive hydraulic pressure to
the lift cylinder assembly 29 the clamp release pin 67 will be
extended downwardly to apply a force upon the platform 68 of
the bowl clamp ring 37, thus driving this ring downwardly to
break its clamping or wedging action between the bowl assembly
and bowl support ring 31. Each clamp release pin 67 carries
a pin seal 70 surrounding the pin adjacent the juncture between
the cylinder unit ~4 and the pin to preclude the entrance of
foreign material into the bowl support ring aperture 66, while
a separate ring seal 71 is carried by the upper portion of the
bowl clamp ring 37 and constantly wipes or engages the outer
periphery 26 of the bowl assembly cylindrical body to prevent
the entrance of any dirt or foreign material between the inner
surface 39 of the clamp ring 37 and bowl assembly outer peri-
phery 26, it being readily appreciated that any foreign material
admitted between the clamping surfaces of the clamp ring 37
would be detrimental to the accomplishment of a positive tight
interlocking of the involved components.
The massive weight of the entire bowl assembly 4 and
the associated clamping means comprising the segmented ring 37
and bowl support ring 31 and the attendant structure previously
described herein is supported upon the upper portion or ~-way
104 of the peripheral frame 1 by means of the male tapered
support surfaces 30-30 engaging the female tapered support
surfaces 35-35 of the bowl support ring 31. ~eans must be
-12-
~577~8
1 provided to prevent jamming or damage to the crusher part~ upon
the introduction of tramp iron or other non-crushable material
into the apparatus. Such means comprise a plurality of shock
load relief cylinders, generally designated 72, fixedly attached
to the frame of the crusher immediately beneath the bowl support
ring 31 in an equi-distant manner. A total of nine such cylinders
has been found to be most desirable. Each load relief cylinder
amounts to a hydraulic shock absorber and includes a fixed
cylinder unit 73 containing a vertically displaceable piston
unit 74 between which is defined a fluid chamber 75. As will be
seen in FIG. 2, the piston unit 74 is spherically seated on and
contained by the lower end of a tie bolt 76, the upper portion
of which freely passes through an aperture 77 in the upper
portion of the peripheral frame 1 as well as an overlying aper-
ture 78 through the bowl support ring 31. The upper end of thetie bolt 76 terminates in a tie bolt nut 79 adapted to overlie
and engage the top surface 32 of the bowl support ring 31.
Associated with each load relief cylinder 72 is a
hydraulic accumulator 80 shown most clearly in FIGS. 1 and 3
and which is connected by a hydraulic relief tube 81 which
communicates with the upper portion of the fluid chamber 75 of
its associated relief cylinder 72. The upper portion of each
fluid chamber 75 is additionally connected by means of a separate
relief cylinder series line 82 to the upper portion of each adjacent
fluid chamber 75 such that it will be seen that all of the
plurality of load relief cylinders 72 have the upper portion of
their fluid chambers 75 communicating with one another in series
while each load relief cylinder directly communicates with its
own separate fluid accumulator 80. The above structure will be
understood to provide an improved shock load relief system
la~s77~8
1 whereupon when tramp iron or other non-crushable material is
trapped between one point of the bowl liner 3 and an adjacent
point on the gyrating mantle 2 the radially adjacent portion
of the bowl support ring 31 will be urged upwardly with the
result that the support ring top surface 32 will elevate the
tie bolt nuts 79 thereby causing a corresponding elevation of
its attached piston unit 74. ~his vertical displacement of the
load relief piston will, of course, meet the resistance of the
hydraulic fluid contained within the respective fluid chambers
75. During this displacement a small portion of the displaced
fluid will be ejected from the respective fluid chamber 75
through the two series lines 82-82 leading from this cylinder
to the next two adjacent load relief cylinders 72-72 and at
the same time a significant portion of the displaced fluid will
be ejected through the single hydraulic relief tube 81 leading
from this load relief cylinder to its associated accumulator
80. ~uite obviously, the resistance offered by the above action
of the load relief cylinder 72 will be controlled by the
pressure setting of the related accumulators 80.
The above description relates to the displacement
action attendant to only a single load relief cylinder 72
during the entrapment of tramp iron within the crusher, yet
it will be appreciated that at any time when one point o~ the
bowl support ring 31 is elevated, other circumferentially
spaced points of the support ring will likewise be elevated,
to various degrees. The greatest vertical displacement of the
bowl support ring 31, of course, occurs directly radially out-
ward ~f the point of entrapment of non-crushable material with
a lesser degree of vertical displacement thereof occurring as
one circumferentially follows this point about the remainder of
-14-
lnS~r~l~
the bowl support ring so that the least amount of displacement
of the bowl support ring 31 occurs at a point diametrically
opposed the maximum degree of displacement.
Reference may be made to FIG. 8 for an illustration
of this variance in displacement of the bowl support ring 31.
In this figure the right hand portion thereof illustrates a
typical example of the relative position between the bowl
support ring 31 and top portion of the peripheral frame 1 at a
point substantially adjacent the greatest degree of bowl support
ring vertical displacement while the left hand portion of this
figure illustrates the relative position of the crusher com-
ponents at a point 180 from the point of maximum displacement.
The center illustration in FIG. 8 represents the relative
positioning of the bowl support and peripheral frame at a point
intermediate to the points of maximum and minimum displacement.
Also shown in this figure is the provision of a guide or align-
ment pin generally designated 83. A plurality of these pins 83
are provided about the circumference of the bawl support ring
31 equi-spaced thereabout and intermediate the load relief
cylinders 72. Each guide pin 83 includes a mounting shar~c 84
disposed within the bawl support ring 31 intermediate the fe-
male tapered support surfaces 35-35 thereof and secured to the
support ring by means of an attaching bolt 85. A cylindrical
body section 86 depends from the shar~c 84 and terminates in a
tapered body section 87. The normal disposition of the guide
pins 83 closely approximates the relationship as is shown in
the left hand portion of FIG. 2 wherein it will be appreciated
that during normal operation of the crusher all of the plurality
of guide pins 83 are disposed with the central body sections 86
and tapered body section~ 87 centrally located within the
l~S7'7~
1 confines of vertical apertures 88 formed in the upper portion
of the peripheral frame 1 intermediate the male tapered support
surfaces 30-30 thereof. The inclination of the tapered body
section 87 of the guide pins 83 is selected to ensure that
~henever the relief cylinders 72 are actuated by vertical displace-
ment of the support ring 31, the tapered body sections 87 will
not engage or bind with the side of the vertical apertures 88
through the peripheral frame 1, This is shown most clearly in
FIG. 8 wherein it will be seen that the periphery of the tapered
body sections 87 of the three guide pins 83 are disposed sub-
stantially parallel to the vertical apertures 88 when the bowl
is tilted. This relationship is achieved due to the combined
elevation and tilting of the vertical axes of the various guide
pins during tilting of the bowl assembly 4 and as shown in the
left hand portion of FIG. 8 the lowermost portion of the outer
female tapered support surface 35 serves as a fulcrum 89 in the
area which is substantially 180 from the point of maximum verti-
cal displacement of the bowl support ring 31.
The hydraulic inter-action between all of the load
relief cylinders 72 as well as each individual accumulator 80
associated with each load relief cylinder has been described
hereinabove. As previously mentioned, the three lift cylinder
assemblies 29 are adapted to be supplied with hydraulic fluid
under pressure as are the three shim stud hydraulic washers 46'.
As sh~n most clearly in FIGS. 1 and 3, a lift cylinder assembly
conduit 90 supplies hydraulic fluid to all of the three lift
cylinder assemblies 29 in a series manner from a suitable regu-
lateable hydraulic supply means (not shown). A separate hydrau-
lic washer conduit 91 similarly leads to all of the hydraulic
washers 46 and 46' in a series manner and is likewise connected
lUS77h8
1 to a suitable hydraulic supply source (not sho~n).
Re~erence will now be made to the anti-spin assembly
generally designated 92 and which is illustrated in FIGS. 2, 4
and 5. As is well known to those skilled in the operation of
gyratory crushers, when there is no feed material being delivered
to the crushing chamber and the drive shaft 18 is running, the
head 5 spins during gyration thereof. This action is due to
friction in the bearings located between the head 5 and eccentric
9, and is detrimental to the efficient operation of the crusher
when feed material is again admitted to the crushing chamber
since a high degree of scuffing and wear of the crushing elements
will occur. Anti-friction means for precluding this spinning
of the crusher head in the same direction as the eccentric are
generally well known in this type of crusher and the present
anti-spin assembly 92 has been constructed to provide an improved
operation.
A hydraulic fluid pump, generally designated 93, is
fixedly mounted in the lower portion of the stationary vertical
bearing shaft 14 and extending upwardly therefrom is a teles-
coping propeller shaft 94 comprising upper section 95 and lower
section 96. An upper universal joint 97 connects the top of
the upper section 95 to the mantle bolt 6 while a lower U-joint
98 connects the bottom of the lower section 96 to the internal
rotary gear mechanism of the fluid pump 93. The pump 93 contains
a check valve 99 opening into an oil chamber 100 completely
surrounding the pump 93 and which is constantly supplied with
oil under pressure by means of a suitable pump (not shown)
located outside the crusher and which supplies oil to the chamber
by means of a fluid inlet 101 in the crusher frame. The one-
way ~heck valve 99 serves as an inlet port when the shaft 94
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~' - ~
1~i77~8
1 rotates in one direction during the normal crushing operation
and all fluid drawn into the pump by the gear therein (not shown)
is ejected through another port 99' and into the chamber 100.
on the other hand, during a no-feed condition when the head S
S and shaft 94 tend to rotate in the opposite direction, along
with the connected gear of the pump 93, fluid is drawn into the
pump through the port 99' and meets the resistance of the check
valve 99 and bypasses the pump gear to allow very slow rotation
of the shaft 94 and head 5. Thus, by means of the pump 93,
opposite or no-feed spinning motion is restrained, not 100%, but
signficantly, so that there will be no damage to the bowl liner
3 and mantle 2 when feed material is again introduced into the
crushing zone therebetween.
The inlet 101 serves to provide oil not only to
lS surround and supply the pump 93 within the chamber 100, but also
to provide oil for lubrication of all relatively moving compon-
ents of the crusher. From a review of FIG. 2 it will be apparent
that oil admitted to the central bore 102 of the vertical
bearing shaft 14 will be pumped upwardly therethrough and thence
cascade downwardly through the radial and thrust bearings before
returning to the sump as formed by the bottom of the base frame
12 and oil outlet 103 connected to a suitable pump (not shown).
-18-
