[0001] This invention relates to vertical shaft impact crushers, and particularly to protective
guard rings for such crushers to protect against the abrasive action of rock fragments
and rock dust.
[0002] The vertical shaft impact crusher has a cylindrical rotor which rotates on a vertical
axis within a crusher tank and throws rock, which is fed axially into the rotor, radially
outward against a breaker ring where the rock shatters and falls through an opening
in the bottom of the tank. Crushers of this variety are relatively inexpensive and
reliable and are in wide use because their advantages are well recognized. However,
there are some defects in existing vertical shaft impact crushers which have retarded
their adoption by the industry, because the inefficiencies which they introduce tend
to offset the inherent advantages of this type of crusher.
[0003] A problem with prior art vertical shaft impact crushers is intrusion of rock dust
or rock fragments into the radially interior region and into the environment of the
bearing cartridge beneath the rotor. Intrusion of dust and rock particles into the
bearing cartridge can cause damage to the bearing if they actually intrude into the
bearing itself. The rock dust is particularly abrasive and can cause rapid damage
to a bearing. Most bearings have some sort of dust seal, but the dust seal can be
overwhelmed and contaminated with dust if the vicinity of the seal is not maintained
relatively clean.
[0004] Reference is made to US-A-4126 280 which discloses a vertical shaft impact crusher
according to the precharacterizing portion of independent claim 1. The known crusher
has a stationary dust shell surrounding the bearing cartridge and fixed thereto at
its upper end is a seal ring cooperating with the underside of the rotor. Reference
is also made to US-A-3 148 840 wherein an upstanding circular rim is welded to shield
plates carried by bearing support bars. The rim is open at its lower end and is telescopically
received at its upper end within a peripheral wear band of the rotor. No provisions
are made to prevent rock dust from intrusion into the environment of the bearing cartridge
and dust seals.
[0005] The object of the bearing is to provide a vertical shaft impact crusher in which
improved provision is made for protection of the environment of the bearing cartridge
from intrusion by rock dust and particles to protect the bearing dust seals against
contamination with dust.
[0006] This is achieved, in accordance with the invention, by the features recited in the
precharacterizing portion of independent claim 1.
[0007] Advantageous embodiments of the vertical shaft impact crusher are recited in the
dependent claims 2 through 6.
[0008] A more thorough understanding of the present invention will be gained by reading
the following description of the preferred embodiments with reference to the accompanying
drawings in which:
Figure 1 is a perspective view of a vertical shaft impact crusher made in accordance
with this invention;
Figure 2 is a sectional elevation of the vertical shaft impactor shown in Figure 1
with the anvil breaker ring installed;
Figure 3 is a partial sectional perspective of the vertical shaft impactor shown in
Figure 1 with the cover and rotor removed and a fragment of the breaker ring exploded
out of the machine;
Figure 4 is a sectional elevation of the bearing cartridge for the vertical shaft
impactor shown in Figure 1 and a portion of the rotor mounted on the top end thereof;
Figure 5 is a sectional elevation of the upper end of a vertical shaft impactor shown
in Figure 1 showing, on the left side, the autogenous breaker ring and, on the right
side, the anvil breaker ring;
Figure 6 is a plan view of the rotor and anvil breaker ring in the vertical shaft
impactor shown in Figure 2;
Figure 7 is an enlarged plan view of the rotor shown in Figure 6;
Figure 8 is an enlarged sectional elevation of the rotor shown in Figure 7; and
Figure 9 is a perspective view of the two wear plates in one quadrant of the rotor
shown in Figures 7 and 8.
[0009] Turning now to the drawings wherein like characters designate identical or corresaponding
parts, and more particularly to Figures 1 and 2 thereof, a vertical shaft impactor
includes a frame 10 on which is mounted a drive motor 12, a crusher tank 14 bolted
to the frame concentrically around a pair of segmental openings 15 therethrough, a
crane 16, and a grease reservoir 18. A bearing cartridge 20 is also mounted directly
to the frame 10 coaxially within the crusher tank 14. The bearing cartridge 20 supports
for rotation about a vertical axis a shaft 22 which has mounted on its top end a rotor
24 and, mounted on its lower end, a sheave 26 which is connected by way of a drive
belt 28 to a corresponding sheave 30 mounted on the lower end of the motor shaft 32.
[0010] A cover 34 is mounted on top of the crusher tank 14 and includes a feed funnel 36
mounted on a collar 38 which is welded to a cover plate 40 concentrically with a central
hole 42 in the cover plate 40. A series of three radially extending tapered braces
44 are welded to the collar 38 and to the cover plate 40 to strengthen the cover and
provide, by virtue of holes 46 in the braces 44, means for attaching a hoist cable
from the crane 16 when it is desired to lift the cover off of the crusher tank 14.
[0011] The feed tube 36 has a floor plate 48 having a central opening 50. A feed tube 52
is welded to the underside of the floor plate 48 and depends downwardly therefrom
to a level approximately equal to the cover plate 40. A replaceable feed tube extension
54 is telescopically disposed around the feed tube 52 and is provided with an extension
adjustment mechanism for adjusting the length of its extension through the hole 42
in the cover plate 40. The adjustment extension mechanism includes an outwardly projecting
flange 56 most clearly shown in Figure 5, and a series of spacers 58 lined between
the flange 56 and the region of the cover plate around the hole 42. The spacers 58
are held in position by a bolt 60 which extends through the flange, the spacers and
the top plate 40. A series of access openings 62 in the collar 38 allows access to
the bolt 60 for removing or adding spacers 58 to change the vertical position of the
feed tube extension 54. The spacers 58 are u-shaped in plan view so that there is
no need to remove the bolt 60 when adding or removing spacers.
[0012] A guard shell 63 made of a series of shell segments 64 is bolted to the underside
of the cover plate 40 concentrically around the central hole 42. The shell segments
are arcuate in form and include an inwardly extending upper flange by which the segments
64 are bolted to the cover plate. The liner segments 64 protect the top of the rotor
24 from damage by broken rock bouncing off of a breaker ring 70 mounted in the crusher
tank 14 horizontally aligned with the rotor 24.
[0013] The breaker ring 70 shown in Fiugre 2 and shown in greater detail in Figures 3, 5
and 6 includes an annular hoop 72 of heavy steel construction having an annular seal
73 fastened to its top surface for sealing the space between the hoop 72 and the crusher
tank 14. Three depending vertical legs 74 are welded to the underside of the hoop
72 at equally spaced angular positions around the hoop. The legs 74 are supported
by three stepped mounting blocks 76 welded to the inside of the crusher tank 14, as
shown most clearly in Figure 3. The support blocks 76 have a plurality of steps formed
thereon at different angular positions and elevations to provide a plurality of elevation
settings for the breaker ring. This enables the elevation of the breaker ring to be
adjusted within the crusher tank 14 so that the vertical position of the breaker ring
relative to the rotor can be optimized for optimal breaking efficiency and use of
material, as explained more fully below.
[0014] The breaker ring 70 has welded thereon a series of brackets 78, each having two legs
77 fastened to and extending inwardly from the hoop 72 on a secant to the circle defined
by the hoop. A cross arm 79 is welded to and extends between the outside ends of each
pair of legs 77 and has a vertical slot 81 completely through the arm 79. The cross
arm 79 is actually made of two separate pieces, one each welded to the end of each
leg 77. Three lifting lugs 75 are welded to three legs 77 at equally spaced angular
positions around the breaker ring for attachment of a cable to hoist the breaker ring
in and out of the tank 14.
[0015] An anvil 80 is supported by each bracket 78. Each anvil 80 includes an octagonal
head 82 having a flat octagonal face 83, a square foot 84, and a square neck connecting
the head 82 and the foot 84. The head, foot and neck of the anvil 80 are symmetrical
about a horizontal axis 88 forming an angle a with the tangent 87 of the rotor through
the anvil of about 5-15°, with 10° being preferred as shown in Figure 6. This angle
represents the radial component of velocity exerted by the rotor on the rock as it
is propelled from the rotor. The radial component of velocity is a function of the
rotor pocket face angle, as discussed below.
[0016] Each anvil 80 is supported on a bracket 78 by lowering the anvil neck 87 into the
slot 81 in the cross arm 78 until the anvil foot 84 contacts a support plate 89 welded
to the bottom of the bracket legs 77 and cross arm 79. The support plates 89 support
the vertical weight of the anvils 80 and also rigidify the brackets 78.
[0017] The brackets 78 are welded from simple flame- cut pieces for great economy and precision
of manufacture, and also great strength. The anvils 80 each weigh about 200 lbs. and
it is desirable that they be held securely to the breaker ring. The pieces all overlap
each other slightly to provide convenient and economical outside rabbets in which
the pieces can be quickly and securely welded. The structure is so open and accessible
that it is particuarly suitable for automatic welding operations.
[0018] The octagonal faces 83 of the anvil heads 82 represent an efficient utilization of
anvil material, since the corners of a square or rectangular anvil are not impacted
by rock in a centrifugal impact crusher. The octagonal face is symmetrical about the
axis 88 of the anvil so that the anvils may be rotated by multiples of 90° without
changing the pattern of anvil faces presented to the rotor 24. It is thus possible
to maintain a substantially uniform and consistent anvil array throughout the useful
life of the anvil.
[0019] The support blocks 76, spaced at equal angular positions around the crusher tank
14, enable the breaker ring 70 to be rotated to as many positions as there are support
blocks 76, three being disclosed herein. In practice, the rocks tend to be thrown
predominantly in one angular region because they tend to fall into the rotor predominantly
toward one side because of the conveyor feeder. Consequently, the anvils 80 in that
one angular region tend to wear faster than in other regions. By periodically rotating
the breaker ring incrementally, it is thus possible to distribute the anvil wear more
evenly.
[0020] The rotor, as seen in Figures 2 and 6 through 9, includes a circular base plate 90
having an axial hub 92 formed integrally on the vertical centerline 94 of the rotor.
A top plate 96 is disposed vertically above and parallel to the base plate 90 and
coaxial therewith. The top plate 96 is held in spaced relationship to the base plate
90 by a series of vertically oriented partitions or plates which form four autogenous
pockets 98 spaced equally around the rotor. Each pocket 98 is formed of an arcuate
circumferential or peripheral plate 100 and a radial plate 102 welded to the trailing
end of the circumferential plate 100 in the sense of the direction of rotation thereof.
A pocket floor plate 104 is welded at an angle y of about 76° between the radial plate
102 and the arcuate plate 100. The angle y is selected to lie approximately parallel
to the top face 106 of the dirt and rock bed which collects and is held in the pocket
98 while the machine is in operation, although the angle of face 106 may be adjustable
by the technique disclosed below. The pocket floor plate 104 reduces the mass of the
rock bed in the pocket to minimize the severity of the imbalance if one rock bed becomes
dislodged.
[0021] The leading edge of each arcuate plate 100, on the end remote from the end to which
the radial plate 102 is connected, has attached thereto a wear resistant bar 110.
The wear resistant bar 110 is attached to the leading edge of the arcuate plate 100
by two bolts 112 which pass through a back-up bar 114 on the outside of the arcuate
plate 100 to protect the bolts 112 from erosion by broken rock ricocheting off the
anvils 80. The leading inside edge of the wear resistant bar 110 includes a slot in
which is fixed, as by silver soldering, a piece of hard wear resistant material 116
such as silicon carbide.
[0022] The radial inside edge of the radial plate 102 is protected from erosion by a wear
bar 118. The wear bar 118 is an L-shaped member which is held in place on the radial
plate 102 by tack welding and is removed by burning through the tack welds with a
torch. The wear bar 118 is made of a high chrome steel and does not require the silicon
carbide insert as used in the wear bar 110 because the wear bar 118 is much closer
to the axis of the rotor than the wear bar 110, so it is not subjected to the same
degree of errosive action that the wear bar 110 experiences as rocks are accelerated
off its leading edge.
[0023] The angle selected for the face 106 of the rock bed in the pocket 98 is controlled
by length of the radial plate 102 and the effective length of the peripheral arcuate
plate 100. The effective length of both plates can be varied by the use of different
wear bars 110 and 118 having greater length so they effectively extend either the
radial plate 102 (for a smaller angle of the face of the rock bed) or the arcuate
plate 100 (for a greater angle of the rock bed face).
[0024] To increase the shattering effect of the
'rotor itself on the rock, it may be desirable to replace the autogenous rotor pocket
structure with conventional cast iron impeller shoes. The rotor 24 of this invention
will accommodate the installation of conventional shoes mounted directly to the walls
100, 102 and 104, or could be mounted directly to the rotor base plate 90 in place
of the autogenous pocket walls.
[0025] A pair of wear plates 120 and 122 is fixed to the rotor base plate 90 and the rotor
top plate 96, respectively, in each of the four quadrants of the rotor. The bottom
wear plate 120 is fixed to the top surface of the rotor base plate 90 by a pair of
bolts 124 which pass through the wear plate 120 and the rotor base plate 90 and are
locked into position by suitable locking nuts such as
øbeam nuts 125 or the like. The upper wear plate 122 is fixed to the underside of the
rotor top plate 96 by a pair of bolts 126 which pass through the wear plate 122 and
the top plate 96 and are held into position by similar beam nuts 125. The portion
of the upper wear plate nuts 125 and bolts 126 which project above the top surface
of the rotor top plate 96 are protected from erosion by ferrules 128 which are welded
to the top surface of the top plate 96 coaxial with the bolts 126.
[0026] As shown in Figure 9, the bottom and upper wear plates 120 and 122 have an arcuate
outer edge 130 and 132, respectively, which conforms to the outer circumferential
configuration of the rotor base plate 90 and the rotor top plate 96, respectively,
and arcuate radial inner edges 134 and 136, respectively, which are at different radii
from each other. The plates 120 and 122 are otherwise identical. The radius of the
inside edge 136 of the upper wear plate 122 is equal to or slightly smaller than the
radius of the central opening in the rotor top plate 96, and the radius of the inside
edge 136 of the bottom wear plate 120 is equal to the radius of a protective cap 138.
which is bolted to a cover plate 140 which lies over the top of the hub 92. The other
three edges of the wear plates 120 and 122 are straight and orthogonally oriented
so that the wear plates may be slid straight into and out of the rotor when they are
being replaced.
[0027] The plates 120 and 122 are simple designs that are easy to manufacture economically.
They can be made from rectangular plates by flame cutting an outside radius on one
side which will be the same for both top and bottom plates, and a circular arc on
one corner concentric with the outside radius. The cutting can be done at high volume
and low expense by automated ganged plasma arc. The plates are very easy to handle
because they are flat and can be stacked flat or on edge.
[0028] A protective skirt or lower outer guard ring 142 is tack welded around the outside
periphery of the rotor base plate 90, projecting vertically slightly above the top
surface thereof and vertically below the top surface thereof a distance approximately
equal to the thickness of the rotor base plate 90. The skirt 142 protects the edge
of the rotor base plate 90 from erosion and also provides a shoulder by which the
position of the bottom wear plate 120 can be located for ease of insertion of the
bolts 124 when the wear plate 120 is replaced. The bottom extension of the skirt 142
protects the lower projection of the bolts 124 and the nuts 125 from erosion by rock
fragments ricocheting off of the anvils 80.
[0029] The skirt 142 is attached to the rotor base plate 90 by placing a split, which becomes
the skirt 142 after attachment, around the base plate 90 and supporting it in position
for welding or other fusion joining, such as brazing. The annular hoop has a diameter
slightly smaller than the diameter of the base plate 90 so there is a gap between
adjacent edges of the hoop at the split when it is placed on the base plate 90. The
hoop is then tack welded to the base plate 90 at the shoulder formed at the junction
of the lower outside edge of the rotor base plate 90 and the hoop adjacent to one
edge of the hoop at the split. The hoop is progressively tack welded to the base plate
90 aorund the full circumference of the hoop. The welding heats the hoop so that it
thermally expands and the gap at the parting line closes as the hoop gets hot. At
the conclusion of the tack welding, the hoop is welded closed at the parting line
to produce a full circumferential skirt 142 which is welded and shrunk fit to the
rotor base plate 90 for secure attachment.
[0030] A top guard rind or rim 144 is welded to the rotor top plate 96 in the same manner
used to weld the protective skirt 142 to the rotor base plate 90. The top of the top
rim 144 projects above the top surface of the top plate 96 and forms a shoulder 145
therewith. The guard shell 63 extends down from the cover 34 just inside of and closely
adjacent to the top rim 144. The closely spaced top rim 144 and guard shell 63 cooperate
together in the manner of a labyrinth seal to restrict the entrance of rock chips
and dust from the region above the rotor where they could cause errosive damage to
the rotor top plate and adjacent structures.
[0031] The skirt 142 and the top rim 144 provide a prestressed support ring to radially
support the wear plates 120 and 122. Under high centrifugal force, the skirt and rim,
if not prestressed, could expand slightly and lessen the radial support provided to
the wear plates. Although the bolts 124 and 126 are sized to hold the wear plates
in place, the prestressed skirt and rim provide additional security to relieve the
load on these bolts.
[0032] When the skirt 142 and rim 144 become worn, they are easily replaced during servicing
of the rotor by burning out the tack welds which hold the skirt and rim to the rotor
base plate 90 and top plate 96, and then welding on a new pair. When the wear plates
120 and 122 become worn, they are easily removed by removing the bolts 124 and 126
and sliding the wear plates out over the protective lip provided by the skirt 142
and top guard ring or rim 144. The parallel edges of the wear plates facilitate easy
removal and replacement. it is an advantage to be able to replace the guard rings
and wear plates separately only when they become worn. Even through the replacement
procedure is very fast, the cost of the replacement parts is better saved if there
is useful life remaining in the part.
[0033] As is shown most clearly in Fig. 8, the rotor hub 92 is held to the top of the shaft
22 by a tapered collar 146 having a lower radial flange 148. A series of tapped holes
in the flange 148 threadedly receive the threaded ends of bolts 150 which extend through
aligned holes in the cover plate 140 and the hub 92. The collar 146 may be slotted
at 152 to receive a key on the end of the shaft 22. The bolts 150 are tightened to
force the tapered collar 146 into the tapered bore of the hub 92 which squeezes the
collar down against the shaft to firmly lock the rotor 24 onto the end of the shaft
22.
[0034] The shaft 22 is supported by a cylindrical bearing cartridge 20 shown best in Fig.
4: A heavy cylindrical cartridge housing 154 is attached to a bridge 155 in the base
between the two segmental openings 15 by bolting a lower flange 156, integral with
the housing 154, and in which is drilled a plurality of holes 158 which receive bolts
160 by which the bearing cartridge housing 154 is fastened to frame bridge 155.
[0035] A lower cartridge closure 162 is bolted to the lower axial end of the housing 154
coaxially with the housing axis. A special ring 163 is held on the lower end of the
shaft 22 with a suitable set screw or the like, and includes a flange 165 having a
labyrinth seal configuration on its upper surface which mates with a complementary
labyrinth seal configuration on the lower surface of the lower cartridge closure 162.
The cartridge closure 162 has a shoulder 164 which receives the outside race 166 of
a thrust bearing 168. The weight of the shaft and the rotor which it supports is borne
on the inside race 170 of the thrust bearing 168. The shaft load is exerted on the
inside race 170 through the inside race 172 of a radial bearing 174 positioned immediately
above the thrust bearing 168. The shaft load is carried by the inside race 172 by
virtue of its engagement with a shoulder 176 on the shaft 22.
[0036] A radial bearing 180 provides radial support of the shaft 22 at the top end of the
bearing cartridge housing 154. A bearing cup 182 is supported on an inside shoulder
184 on the inside of the bearing cartridge housing 154. The bearing cup 182 restricts
drainage of lubricant from the top radial bearing 180. A top cartridge closure 186
is bolted to the top of the bearing cartridge housing 154 and includes on its top
inner periphery a labyrinth seal configuration which mates with a corresponding labyrinth
seal configuration on the lower face of a flange 188 on an annular seal ring 190 which
seats on a shoulder 192 on the shaft 22. When the rotor is placed onto the top end
of the shaft 22, the weight of the rotor is borne on the seal ring 190 and the weight
is transmitted to the shaft 22 through the engagement of the lower end of the seal
ring with the shoulder 192 on the shaft 22.
[0037] A cylindrical dust shell 194 surrounds the bearing cartridge 20 and is supported
thereon by a radially inwardly extending flange 196 which is bolted to a radially
outwardly extending flange 198 adjacent the top of the cartridge housing 154. A rubber
bumper 200 is fitted on the lower end of the dust shell 194 and is slightly compressed
between the dust shell and the frame 10 to exclude dust from the bearing cartridge
and to dampen vibration and minimize noise. A urethane shield 202 is secured to the
outside surface of the dust shell 194 to prevent abrasive damage to the dust shell
and also to dampen vibration and minimize noise. The urethane shield 202 may be bolted
to the dust shell or may be bonded directly to the shell.
[0038] A lower inner dust guard ring 203 is welded to the underside of the rotor base plate
90 concentric with the rotor axis, adjacent to and outside of the dust shell 194,
and immediately above the urethane shield 202. The close spacing, of the guard ring
203 to the dust shell 194 and the shield 202, and the rotation of the guard ring relative
to the stationary shell and shield tends to exclude dust so that the interior of the
dust shell 194 stays clean. All of the outside guard rings, namely, the skirt 142,
the top rim 144 and the dust guard ring 203 are attached to the rotor 24 and rotate
with it. Since most rock fragments that strike the guard rings on the rebound from
the anvils 80 will have a component of velocity in the direction of rotor motion,
the errosive action of the rock on the guard rings will be lessened.
[0039] The bearing cartridge is sealed and lubricated by an automated grease injection system
that injects grease from the reservoir 18 into the labyrinth seals for sealing and
into the bearings for lubrication. The grease injection system includes a grease line
204 which runs from a grease distributor 206 to a fitting 208 through which the grease
is conveyed into and through a radial passage 209 in the top cartridge closure 186
to the annular space immediatley above the top radial bearing 180. The lower radial
bearing 174 and the thrust bearing 168 are lubricated through a grease line 210 which
runs from the grease distributor 206 to a fitting 212 on the cartridge housing 154
through which grease is conveyed to and through a radial passage 214 in the housing
154 to the space immediately above the radial bearing 172. Grease works through the
lower radial bearing 174 and into the thrust.bearing 168.
[0040] The upper and lower grease seals utilize the labyrinth seal configuration between
the upper and lower seal rings 190 and 163, and the upper and lower cartridge closures
186 and 162. Grease passages 215 and 216 in the cartridge closures 186 and 162, respectively
are connected by grease lines 217 and 218 to the distributor 206 for injection of
grease into the labyrinth seal cavities to prevent the entrance of stone dust or other
abrasive foreign matter into the bearing housing, which could damage the bearings.
The grease is injected into the bearings and the seal cavities by a pump 219 controlled
by a timer 220. The timer causes the pump to operate periodically and the distributor
206 causes the grease to be distributed evenly through each of the four lines so that
grease is distributed to the seals and the bearings for certain lubrication and sealing
action. If there is a failure in the distributor or the pump, an internal alarm operates
to alert the operator of the problem so that corrective action may be taken immediately.
[0041] The use of a common grease injection system for both sealing and lubrication greatly
simplifies and improves the bearing system. Conventional lubrication uses an oil circulation
system for flushing dirt and heat out of the bearing, but such a system is more expensive
than the grease system disclosed herein because it requires an oil return and filter
network, continuous pump operation, and is more susceptible to_ catastrophic bearing
failure in the event of pump malfunction. By properly sizing and sealing the bearings
in this application, a simple, reliable and inexpensive grease lubrication has been
provided that positively seals and lubricates using the same fluid.
[0042] Referring now to Figs. 2 and 3, the crusher tank 14 is a cylindrical tank having
a rubber bumper 222 placed on the top lip of the tank to act as a dust seal and also
to dampen vibration and attenuate noise. An annular bracket 224 is welded around the
outside surface of the tank slightly below the top lip and provides a support to which
the bottom edge of a plurality of upright locking tongues 226 are welded. Each of
locking tongues has a rectangular hole 228 punched in its upper end for receiving
a lock wedge 230. The cover plate 40 has a series of short radial slots 232 at its
outside edge at angular positions corresponding to the angular positions of the locking
tongues 226 around the tank 14, so that when the cover is placed on the top of the
tank 14 with the locking tongues lined up with the slots 232, the tongues 226 will
extend through the slots 232 and the lock wedges 230 may be driven into the holes
228 to lock the cover in place.
[0043] A series of spacer blocks 234 is welded on a horizontal line around the inside of
the tank just beneath the stepped support blocks 76. The spacer blocks 234 are each
drilled and tapped to accept a bolt 236 which fastens a rubber curtain 238 at its
top edge to the spacer blocks. The rubber curtain 238 hangs down to the floor around
the full inside circumference of the crusher tank 14. It prevents abrasion to the
tank wall and is extremely effective in damping vibration and noise during operation.
[0044] The anvil breaker ring 70 can be removed by attaching a cable hook to each of three
lifting lugs 75 attached to three bracket legs 77 at equally spaced positions around
the annular hoop 72 of the breaker ring 70, and lifting the breaker ring out of the
crusher tank 14. The breaker ring 70 may be replaced with a similar breaker ring 70
or may be replaced with an autogenous breaker ring 70' shown in cross section on the
left-hand side of Figure 5. The autogenous breaker ring 70' is an inwardly opening
channel which is arranged horizontally opposite the rotor 24 for receiving and holding
rock thrown by the rotor so that additional rock will impact the rock in the autogenous
breaker ring 70' and the rock breaking action will be rock on rock rather than rock
on metal.
[0045] The autogenous breaker ring 70' includes an annular cylinder 242 to the top and bottom
of which are welded an annular top disk 244 and annular bottom disk 246, respectively.
The top disk 244 is of a slightly larger radius than the bottom disk and extends almost
to the inside surface of the crusher tank 14. A full annular seal 248 is fastened
to the top of the top disk 244 for the same purpose as the seal 73, namely, to prevent
rock and dust from settling down behind the breaker ring 70' and falling between the
rubber curtain 238 and the crusher tank 14. The seals 73 and 248 also prevent rock
from becoming wedged between the breaker ring and crusher tank 14 when the breaker
ring is lifted out of the tank so that rocks do not become jammed between the ring
and the tank 14. Three equally spaced lifting lugs 249 are welded to the top surface
of the top disk 244 for use in hoisting the breaker ring 70' into and out of the tank
14.
[0046] Three legs 250 are welded to the outside surface of the annular cylinder 242 for
supporting the autogenous breaker ring 70' on the stepped support blocks 76. The vertical
extension of the annular cylinder 242 on the autogenous breaker ring 70' is greater
than the vertical extent of the annular hoop 72 of the anvil breaker ring 70 so that
space between the cylinder 242 and the inside wall of the crusher tank 14 accommodates
the upper steps of the stepped support blocks 76 when the autogenous breaker ring
is set on the lower steps.
[0047] The crane 16 includes a support pillar 254 to which a pair of brackets 256 are attached
for supporting a crane control box 258 by which the crane 16 is controlled. A bearing
(not shown) around the upper portion of the support pillar 254 rotatably supports
the upper end of the crane 16 which includes a vertical extension 260 and a cantilevered
horizontal arm 262. A support bracket 264 is welded to the lower end of the vertical
extension 260 and supports an electric motor 266 coupled to a gear pump 268.
[0048] A hydraulic rotation motor (not shown) is coupled between the upper portion of the
crane 16 and the support pillar to allow the upper portion of the crane to be rotated
about the support pillar. A hydrautic winch motor 270 is coupled to a hydraulic winch
272 which allows a hook 274 to be raised or lowered by taking up or playing out cable
from a winch drum 276.
[0049] The power functions of the crane 16 are controlled from the control box 258 which
contains pilot valves or electric switches for controlling the control valves 278
by which motive fluid from the pump 268 is delivered to the winch motor 270 and the
rotation control motor (not shown).
[0050] In operation, rock to be crushed is continuously fed into the feed funnel 36 and
falls through the feed tube 52 and the feed tube extension 54 and into the center
of the rotor 24. The rotor rotates at a speed on the order of about 1,000 RPM which
throws the rock radially outward where it is caught and accelerated by the rotor pockets
98. The rotor pockets are covered with a blanket of rock which is held within the
pocket to protect the pocket members from erosion by the rock as it is thrown outward.
The only surfaces which encounter erosion within the pocket are the top and bottom
wear plates 122 and 120 and the inner and outer wear bars 118 and 110. These wear
pieces are all easily and quickly replaceable when they wear down.
[0051] The rock is thrown by the pockets 98 outward against either the anvil breaker ring
70 or the autogenous breaker ring 70'. The trajectory of the rock is shown in Figure
6 and is about 5-15
0 out from the tangent to the rotor. The deviation from tangential trajectory is caused
by the angle of the rock face within the pocket 98 and coefficient of friction of
the rock on rock as the rocks are thrown radially outwardly. The brackets 78 are set
in the breaker ring 70' at an angle such that the faces of the anvils 80 lie perpendicular
to the flight trajectory of the rock which is about 10° out of the tangent to the
rotor. In this way, the rocks will strike the anvil faces exactly perpendicular so
that the full momentum of the rock is converted to an internal shattering force and
little of the energy is wasted on ricochet force.
[0052] The broken rock then falls vertically downward between the rubber curtain 238 and
the dust shell 194 and falls through the openings 15 on the two sides of the cartridge
support ridge 155. The rock is then carried away by suitable conveyor belt (not shown).
1. A vertical shaft impact crusher of the type having a frame (10), a rotor (24) supported
within a crusher housing (14) mounted on said frame (10) for rotation about a vertical
axis on a vertical shaft (22) supported by a central bearing cartridge (20) having
an upper peripheral margin, said rotor (24) having a top (96), an underside (90) and
an axial opening (50) through which rock is fed into an impeller chamber (100, 102,
120, 122) which accelerates the rock and throws it outwardly at high speed to impact
against an adjacent breaker means (70) where the rock breaks,
and a stationary dust shell (194) operatively fastened fixedly with respect to said
frame (10) while said crusher is in operation, said dust shell (194) extending vertically
with respect thereto coaxially with said rotor axis and having a height extending
upward, at least to said upper peripheral margin of said bearing cartridge (20) in
close proximity to the underside (90) of said rotor (24) to restrict the entrance
of rock dust and fragments radially into said dust shell (194) and ultimately, into
said bearing cartridge (20),
characterized in that said dust shell (194) is fastened to said bearing cartridge
(20) and that a cylindrical guard ring (203) is fastened to the underside (90) of
said rotor (24) and depends vertically with respect thereto coaxially with said rotor
axis;
said dust shell (194) and said guard ring (203) having portions which nest telescopically
together, said dust shell (194) nesting within said guard ring (203) and said guard
ring (203) being positioned in concentric, axially overlapping rela- tionshipto said
dust shell (194) to provide minimal rotational clearance therebetween.
2. Vertical shaft impact crusher according to claim 1, charcaterized by including
a polymeric shield (202) fastened to the external surface of said dust shell (194)
and extending vertically to a position adjacent to a lower edge of said guard ring
(203).
3. Vertical shaft impact crusher according to claim 1, characterized in that a bumper
(200) is fitted on the lower end of the dust shell (194) and the frame (10).
4. Vertical shaft impact crusher according to claim 1, characterized by including
labyrinth seal means (165, 188) disposed about said shaft (22) and respectively mounted
to the upper and lower peripheral margins of said bearing cartridge (20) to restrict
the entrance of rock dust and fragments into said bearing cartridge (20).
5. Vertical shaft impact crusher according to claim 1, characterized by including
a flexible elastomeric curtain (238) mounted to an inside surface of said housing
(14) in spaced relation thereto and extending to the floor (155) of said housing.
6. Vertical shaft impact crusher according to claim 5, characterized in that said
curtain (238) is secured in spaced relationship to said inside surface of said housing
(14) by a plurality of spacer blocks (234), said blocks being fastened to said housing
(14) along a horizontal line.
1. Senkrechtwellenprallbracher mit einem Rahmen (10), einem Rotor (24), der in einem
auf dem Rahmen (10) befestigten Brechergehäuse (14) zur Drehung um eine senkrechte
Achse auf einer senkrechten Welle (22) befestigt ist, welche durch eine zentrale Lagerhüse
(20) gelagert ist, die einen oberen Umfangsrand hat, wobei der Rotor (24) ein oberes
Ende (96), eine Unterseite (90) und eine axiale Öffnung (50) hat, durch welche .Gestein
in eine Prallkammer (100, 102, 120, 122) eingeführt wird, welche das Gestein beschleunigt
und es mit hoher Geschwindigkeit nach außen schleudert, damit es auf benachbarte Brechereinrichtungen
(70) prallt, wo das Gestein zerbricht, und
einem stationären Staubmantel (194), der in bezug auf den Rahmen (10) feststeht, während
der Brecher in Betrieb ist, wobei sich der Staubmantel (194) in bezug auf denselben
koaxial zu der Rotorachse senkrecht erstreckt und eine Höhe hat, die nach oben hin
wenigstens bis zu dem oberen Umfangsrand der Lagerhülse (20) und bis in unmittelbare
Nähe der Unterseite (90) des Rotors (24) reicht, um das Eindringen von Gesteinsstaub
und -fragmenten radial in den Staubmantel (194) und schließlich in die Lagerhülse
(20) zu verhindern,
dadurch gekennzeichnet, daß der Staubmantel (194) in der Lagerhülse (20) befestigt
ist und daß ein zylindrischer Schutzring (203) an der Unterseite (90) des Rotors (24)
befestigt ist und sich in bezug auf diesen koaxial zu der Rotorachse senkrecht erstreckt;
wobei der Staubmantel (194) und der Schutzring (203) Teile haben, die teleskopisch
ineinandergeschoben sind, wobei der Staubmantel (194) in den Schutzring (203) eingeführt
und der Schutzring (203) in konzentrischer, axial überlappender Beziehung zu dem Staubmantel
(194) angeordnet ist, um minimales Drehspiel zwischen denselben zu schaffen.
2. Senkrechtwellenprallbrecher nach Anspruch 1, gekennzeichnet durch eine polymere
Abschirmung (202), die an der äußeren Oberfläche des Staubmantels (194) befestigt
ist und sich vertikal in eine Position an einem unteren Rand des Schutzringes (203)
erstreckt.
3. Senkrechtwellenprallbrecher nach Anspruch 1, dadurch gekennzeichnet, daß ein Puffer
(200) an dem unteren Ende des Staubmantels (194) und dem Rahmen (10) angebracht ist.
4. Senkrechtwellenprallbrecher nach Anspruch 1, gekennzeichnet durch Labyrinthdichtungseinrichtungen
(165, 188), die um die Welle (22) und an dem oberen bzw. unteren Umfangsrand der Lagerhülse
(20) angeordnet sind, um das Eindringen von Gesteinsmehl und -fragmenten in die Lagerhülse
(20) zu verhindern.
5. Senkrechtwellenprallbrecher nach Anspruch 1, gekennzeichnet durch einen flexiblen,
elastomeren Vorhang (238), der an einer Innenfläche des Gehäuses (14) mit Abstand
von derselben befestigt ist und sich bis zu dem Boden (155) des Gehäuses erstreckt.
6. Senkrechtwellenprallbrecher nach Anspruch 5, dadurch gekennzeichnet, daß der Vorhang
(238) mit Abstand von der Innenfläche des Gehäuses (14) durch mehrere Distanzblöcke
(234) befestigt ist, die an dem Gehäuse (14) längs einer horizontalen Linie befestigt
sind.
1. Broyeur à percussion à axe vertical du type présentant un bâti (10), un rotor (24)
supporté dans l'enceinte du broyeur (14) monté sur ledit bâti (10) pour tourner autour
de l'axe vertical d'un arbre vertical (22) supporté par un carter de palier central
(20), ayant une marge supérieure périphérique, ledit rotor (24) ayant un sommet (96),
un côté inférieur (90) et une ouverture axiale (50) à travers laquelle la roche est
amenée, dans une chambre de projection (100, 102, 120, 122) qui accélère les roches
et les envoie vers l'extérieur à grande vitesse, pour percuter des moyens briseurs
adjacents (70) ou les roches se brisent,
et une coque antipoussière stationnaire (194) fixée fermement par rapport audit bâti
(10) tandis que le broyeur est en fonctionnement, ladite coque antipoussière (194)
s'étendant verticalement par rapport audit rotor et coaxialement avec l'axe du rotor
et ayant une hauteur de prolongement vers le haut au moins jusqu'à la marge supérieure
périphérique dudit carter de palier (20), à proximité immédiate du côté inférieur
(90) dudit rotor (24), pour restreindre l'entrée de la poussière et de fragments de
roche radialement dans la coque antipoussière (194) et enfin dans le carter de palier
(20),
caractérisé en ce que la coque antipoussière (194) est fixée audit carter de palier
(20), et qu'un anneau de protection cylindrique 203 est fixé au côté inférieur (90)
dudit rotor (24) et pend verticalement par rapport à lui et coaxialement avec ledit
axe de rotor,
ladite coque antipoussière (194) et ledit anneau de protection (203) présentant des
parties qui se logent télescopiquement l'une dans l'autre, ladite coque antipoussière
(194), se logeant dans l'anneau de protection (203) et ledit anneau de protection
(203) étant positionné en relation concentrique et à recouvrement axial avec ladite
coque antipoussière (194) pour fournir un jeu minimum en rotation entre eux.
2. Broyeur à percussion à axe vertical selon la revendication 1 caractérisé par le
fait qu'il comprend un bouclier polymère (202) fixé à la surface externe de ladite
coque antipoussière (194) et s'étendant verticalement jusqu'à une position voisine
du bord inférieur dudit anneau de protection (203).
3. Broyeur à percussion à axe vertical selon la revendication 1 caractérisé en ce
qu'on tampon (200) est logé à l'extrémité inférieure de la coque antipoussière (194)
et sur le cardre (10).
4. Broyeur à percussion à axe vertical selon la revendication 1 caractérisé par le
fait qu'il comprend des moyens d'étanchéité du type labyrinthe (165, 188) disposés
autour dudit arbre (22)' et montés respectivement aux marges périphériques supérieure
et inférieure de carter de palier (20) pour restreindre l'entrée de poussière, et
de fragments de roches dans ledit carter de palier (20).
5. Broyeur à percussion à axe vertical selon la revendication 1 caractérisé par le
fait qu'il comprend un rideau élastomère flexible (238) monté sur la surface interne
de ladite enceinte (14), espacé de celle-ci et s'étendant jusqu'au planche (155) de
ladite enceinte.
6. Broyeur à percussion à axe vertical selon la revendication 5 caractérisé en ce
que le rideau (238) est fixé à distance sur la surface intérieure de ladite enceinte
(14) par une série de blocs d'espacement (234) lesdits blocs étant fixés sur ladite
le long d'une ligne horizontale.