Abstrict A spider sleeve and seal apparatus for a gyratory crusher has upper
and lower cylindrical sleeves disposed between the spider and a
vertically slidable piston. Fixed o-rings are located between the
sleeves and the spider, and moving seals are located in the piston.
These seals prevent leakage from the hydraulic ring used to support
the piston and shaft of the gyratory crusher.
Claims What is claimed is:
1. A gyratory crusher, comprising: a shell; a spider supported
by the shell; a piston disposed within the spider; a shaft coupled
to the piston; an upper cylindrical sleeve disposed between the
piston and the spider, the upper sleeve having a first flange; and
a lower cylindrical sleeve disposed between the piston and the spider,
the lower sleeve having a second flange; wherein the lower sleeve
is retained by the spider and the upper sleeve without the use of
other attachment means.
2. The gyratory crusher of claim 1 further comprising: an upper
O-ring disposed between the upper sleeve and the spider; and a lower
O-ring disposed between the lower sleeve and the spider.
3. The gyratory crusher of claim 2 wherein the O-rings remain
intact at a hydraulic pressure of 5000 psi.
4. The gyratory crusher of claim 1 wherein the upper sleeve has
an inner diameter of about 840 mm and an outer diameter of about
880 mm.
5. The gyratory crusher of claim 1 wherein the lower sleeve has
an inner diameter of about 740 mm and an outer diameter of about
780 mm.
6. The gyratory crusher of claim 1 further comprising: a first
moving seal coupled to the piston and the upper sleeve, and a second
moving seal coupled to the piston and the lower sleeve.
7. A gyratory crusher comprising a piston disposed in a spider,
and a sleeve apparatus comprising: an upper cylindrical sleeve disposed
between the piston and the spider, the upper sleeve having a first
flange; and a lower cylindrical sleeve disposed between the piston
and the spider, the lower sleeve having a second flange; wherein
the lower sleeve is retained by the spider and the upper sleeve
without the use of other attachment devices.
8. The gyratory crusher of claim 7 further comprising: an upper
O-ring disposed between the upper sleeve and the spider; and a lower
O-ring disposed between the lower sleeve and the spider.
9. The gyratory crusher of claim 8 wherein the O-rings remain
intact at a hydraulic pressure of 5000 psi.
10. The gyratory crusher of claim 7 wherein the upper sleeve has
an inner diameter of about 840 mm and an outer diameter of about
880 mm.
11. The gyratory crusher of claim 7 wherein the lower an inner
diameter of about 740 mm and an outer diameter of about 780 mm.
12. The gyratory crusher of claim 7 further comprising: a first
moving seal coupled to the piston and the upper sleeve, and a second
moving seal coupled to the piston and the lower sleeve.
13. A gyratory crusher, comprising: a shell; a spider supported
by the shell; a piston disposed within the spider; a shaft coupled
to the piston; an upper cylindrical sleeve disposed between the
piston and the upper sleeve having a first flange; a lower cylindrical
sleeve disposed between the piston and the lower sleeve having a
second flange; a hydraulic cushion in a space defined by the lower
sleeve piston, and the upper sleeve; an upper O-ring disposed between
the upper sleeve and the spider; and a lower O-ring disposed between
the lower sleeve and the spider; whereby the O-rings provide a seal
for the hydraulic cushion such that the need for an additional ring
seal is eliminated.
14. The gyratory crusher of claim 13 wherein the upper sleeve
has an inner diameter of about 840 mm and an outer diameter of about
880 mm.
15. The gyratory crusher of claim 13 wherein the lower sleeve
diameter of about 740 mm and an outer diameter of about 780 mm.
16. The gyratory crusher of claim 13 further comprising: a first
moving seal coupled to the piston and the upper sleeve, and a second
moving seal coupled to the piston and the tower sleeve.
17. The gyratory crusher of claim 13 wherein the O-rings remain
intact at a hydraulic pressure of 5000 psi.
18. A gyratory crusher comprising a piston disposed in a spider,
and a sleeve apparatus comprising: upper cylindrical sleeve means
disposed between the piston and the spider, the upper sleeve means
having a first flange; and lower cylindrical sleeve means disposed
between the piston and the spider, the lower sleeve means having
a second flange; wherein the lower sleeve is retained by the spider
and the upper sleeve without the use of other attachment devices.
19. The gyratory crusher claim 18 further comprising: an upper
O-ring disposed between the upper sleeve means and the spider; and
a lower O-ring disposed between the lower sleeve means and the spider.
20. The gyratory crusher of claim 18 wherein the upper sleeve
means is a cylinder with an inner diameter of about 840 mm and an
outer diameter of about 880 mm.
21. The gyratory crusher of claim 18 wherein the lower sleeve
means is a cylinder with an inner diameter of about 740 mm and an
outer diameter of about 780 mm.
Description FIELD OF THE INVENTION
The present invention relates to rock crushing systems, such as
conical rock crushers or gyratory crushers. More specifically, the
present invention relates to a spider piston sleeve and seal arrangement
for rock crushers.
BACKGROUND OF THE INVENTION
Gyratory rock crushers generally have a downwardly expanding central
conical member which rotates or gyrates within an outer upwardly
expanding frustroconically shaped member typically called a shell.
The shell can be comprised of two or more pieces, e.g., a top shell
and a bottom shell. The central conical member generally has a wearing
cover or a liner called a mantle. A spider assembly rests on the
top shell, forming the top of the support structure for the machine.
A shaft extends vertically through the rock crusher. The shaft
is supported by a bearing in the spider assembly. The central portion
of the shaft tapers inwardly in an upward direction to form the
central conical crushing member. The central portion of the shaft
supports the mantle, which moves with the shaft to effect the gyratory
crushing operation.
The spider assembly is designed to support the shaft while allowing
gyratory movement during operation of the machine. The vertical
position of the shaft with respect to the spider assembly is controlled
by a piston arrangement in the spider assembly. The piston arrangement
is a complex mechanical apparatus including a piston, a bearing,
and an attachment system. The piston is slidably disposed within
the spider assembly. The bearing is supported by the piston and
supports the shaft while allowing gyratory motion. The bearing has
a hemispherical ball disposed in a socket; the hemispherical ball
is lubricated by a lubricant, such as oil. The attachment system
is required to clamp the shaft to the bearing.
The piston is supported by an annular hydraulic cushion that forces
the piston to travel upward when it is filled with fluid. Because
of the mass of the shaft being supported by the piston, the pressure
inside the hydraulic ring is substantial. Seals are required both
above and below the hydraulic cushion to prevent fluid from leaking
downward into the crusher cavity or upward into the spider cavity.
Typically, cylindrical sleeves are used between the piston and
spider to protect the spider from damage due to the motion of the
piston. Therefore, leakage of oil from the hydraulic cushion must
be prevented both between the piston and the cylindrical sleeves,
and between the cylindrical sleeves and the spider. The sleeve and
seal arrangements are complex with respect to the number of parts
required and the difficulty of installation.
One conventional approach to the problem of sealing the hydraulic
cushion has been to use an upper cylindrical sleeve that is installed
from above the spider and a lower cylindrical sleeve that is installed
from underneath the spider. The disadvantage to this approach is
that if the lower sleeve needs to be replaced, it must be accessed
from below the spider assembly, which is difficult because removal
of the spider is required. Conventional sleeve arrangements also
use additional rings to define the top and bottom of the oil cushion,
in addition to the sleeves. The use of these rings is effective
in sealing the space but not desirable because of the additional
parts. A further disadvantage of conventional piston sleeve and
seal arrangements is that both the lower and upper sleeves must
be attached to the spider with additional hardware.
Therefore, it would be advantageous to have a piston sleeve arrangement
that may be installed and replaced from above the piston, i.e.,
"top service". Further, there is a need for a piston sleeve
and seal arrangement that requires fewer parts. Further still, there
is a need for a piston sleeve and seal arrangement that does not
require hardware to install the lower sleeve.
SUMMARY OF THE INVENTION
An exemplary embodiment relates to a gyratory crusher that has
a shell and a spider supported by the shell. The gyratory crusher
has a piston disposed within the spider, and a shaft that is coupled
to the piston. An upper cylindrical sleeve having a flange is disposed
between the piston and the spider. A lower cylindrical sleeve having
a flange is also disposed between the piston and the spider. The
lower sleeve is retained by the spider and the upper sleeve without
the use of other attachment means.
Another embodiment relates to a spider sleeve apparatus for a gyratory
crusher. The gyratory crusher has a piston disposed in a spider.
The spider sleeve apparatus has an upper cylindrical sleeve having
a flange is disposed between the piston and the spider. The spider
sleeve apparatus has a lower cylindrical sleeve having a flange
is disposed between the piston and the spider. The lower sleeve
is retained by the spider and the upper sleeve without the use of
other attachment devices.
A further embodiment relates to a method of installing or replacing
lower and upper cylindrical sleeves for a gyratory crusher. The
gyratory crusher has a shaft supported by a bearing. The bearing
is supported by a piston disposed within a spider. The method of
installing or replacing the lower and upper cylindrical sleeves
includes the steps of removing the bearing, removing the piston,
and installing the lower sleeve by lowering it in from above the
spider. The method includes further steps of installing the upper
sleeve by lowering it in from above the spider, bolting the upper
sleeve to the spider. The method also includes steps of replacing
the piston, and replacing the bearing.
A still further embodiment relates to a gyratory crusher having
a shell and a spider supported by the shell. The gyratory crusher
has a piston disposed within the spider, and a shaft coupled to
the piston. An upper cylindrical sleeve with a flange is disposed
between the piston and the spider. A lower cylindrical sleeve with
a flange is also disposed between the piston and the spider. The
gyratory crusher has a hydraulic cushion in the space defined by
the lower sleeve flange, the piston, and the upper sleeve. An upper
o-ring is disposed between the upper sleeve and the spider. A lower
o-ring is disposed between the lower sleeve and the spider. The
o-rings provide a seal for the hydraulic cushion such that the need
for an additional ring seal is eliminated.
A still further embodiment relates to a spider sleeve apparatus
for a gyratory crusher. The gyratory crusher has a piston disposed
in a spider. The spider sleeve apparatus has upper cylindrical sleeve
means having a flange disposed between the piston and the spider.
The spider sleeve apparatus has lower cylindrical sleeve means having
a flange disposed between the piston and the spider. The lower sleeve
is retained by the spider and the upper sleeve without the use of
other attachment devices.
BRIEF DESCRIPTION OF THE DRAWINGS
An exemplary embodiment will hereafter be described with reference
to the accompanying drawings, wherein like reference numerals denote
like elements, and:
FIG. 1 is a vertical sectional view of a gyratory crusher; and
FIG. 2 is a fragmentary sectional view of a piston seal arrangement.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to FIG. 1 a gyratory crusher 10 can be utilized to crush
rock, ore, minerals, waste, or other material. Gyratory crusher
10 is assembled on a cast steel base or bottom shell 12 having a
central hub 14. Central hub 14 is provided with a vertical bore
18 adapted to receive a cylindrical support shaft 20. The shaft
20 varies in cross section, but extends through the machine into
the spider 46. Drive housing 13 extends outwardly from hub 14 to
enclose a drive mechanism 22. Drive mechanism 22 causes rotation
of an eccentric 24 which directs the gyratory motion of the shaft
20.
A head assembly 26 which is part of the shaft 20 includes a head
member 30 which is covered by a mantle 34. Mantle 34 provides one
of the crushing surfaces of crusher 10.
A top shell 36 projects upwardly from bottom shell 12 and is covered
by a spider assembly including a spider 46. Alternatively, top shell
36 and bottom shell 12 can be a single piece component. Spider 46
receives a piston 82 which houses an end 42 of shaft 20.
Top shell 36 is protected from wear by several rows of concaves
62. Concaves 62 provide the crushing surface opposing mantle 34.
Spider 46 can be attached or rest upon top shell 36. Vertical positioning
of shaft 20 with respect to top shell 36 adjusts the relative position
of concaves 62 with respect to the mantle 34 of the head member
30 thereby adjusting the size of the crushed material exiting crusher
10.
Material to be crushed is supplied through spider 46 which includes
openings for entry of the material into crushing cavity 50. A liquid
flush apparatus (not shown) may be provided for spraying a liquid
such as water toward the crusher cavity 50.
Spider 46 is comprised of spider arms 52 radially extending outward
from the center to the rim of spider 46. A spider cap 54 sits on
the top center of the spider 46. Each of the spider arms 52 is protected
from falling material by a spider arm guard 56. The rim of spider
46 is protected by a rim liner (not shown), also known as a hopper
liner.
Shaft 20 is supported by a bearing 80 within spider 46. The bearing
80 is disposed within piston 82 that travels vertically within spider
46 to adjust the vertical positioning of shaft 20. Piston 82 is
disposed within an aperture 85 of spider 46. Piston 82 is moved
by a hydraulic system. The hydraulic system includes a hydraulic
fluid inlet 84 and a hydraulic fluid ring 86 that is filled to
move piston 82 vertically. A bearing retainer plate 92 is used to
clamp shaft 20 to bearing 80.
In a preferred embodiment, the aperture 85 that houses piston 82
has a lower portion 87 and a middle portion 89. A shelf 91 is disposed
between the lower portion 87 and the middle portion 89. Aperture
85 further has an upper portion 93 and an upper shelf 95.
Referring to FIG. 2 an upper cylindrical sleeve 100 is disposed
between the piston 82 and the spider 46. A lower cylindrical sleeve
108 is disposed between the piston 82 and the spider 46 below the
upper sleeve 100. Sleeves 100 and 108 protect the spider 46 from
damage due to the vertically slidable piston 82. Hydraulic fluid
ring 86 is located between the upper sleeve 100 and lower sleeve
108 with an inner diameter of about 736 mm and an outer diameter
of about 838 mm.
In a preferred embodiment, upper sleeve 100 is a cylinder made
of steel. Sleeve 100 has an inner radius of 419 mm and an outer
radius of 439 mm. Upper sleeve 100 has a flange 102 that is supported
by spider 46 on shelf 95. The distance from the flange to the bottom
of upper sleeve 100 is 685 mm in a preferred embodiment, and the
flange extends 46 mm outward from upper sleeve. Eight bolts 104
thread into spider 46 and are used to secure upper sleeve 100 to
shelf 95. Bolts 104 are M20.times.80.
An o-ring 106 is disposed between upper sleeve 100 and spider 46.
Preferably, the o-ring 106 is located about 50 mm above bottom 101
of sleeve 100. O-ring 106 is made of rubber, and is fixed in place
because sleeve 100 and spider 46 do not move relative to each other.
In a preferred embodiment, lower sleeve 108 is made of steel and
has an inner radius of 368 mm and an outer radius of 389 mm. Lower
sleeve 108 has an outwardly extending flange 110 that extends 43
mm from sleeve 108. Flange 110 rests on lower shelf 91. In a preferred
embodiment, sleeve 108 extends 273 mm from flange 110 to the lower
end of the sleeve.
O-ring 112 is preferably made of rubber and is located about 25
mm below flange 110 between sleeve 108 and spider 46. O-ring 112
prevents flow of oil from hydraulic ring 86 downward between spider
46 and sleeve 108. O-ring 112 is fixed in position between sleeve
108 and spider 46. Sleeve 108 requires no attachment hardware because
it is captive between spider 46 and upper sleeve 100.
Lower sleeve 108 is captive for the following reasons. Flange 110
rests on shelf 91 preventing lower sleeve 108 from moving downward.
Outer surface 109 with a diameter of 389 mm is flush against lower
portion 87 of spider 46 preventing movement of cylinder 108 in a
horizontal direction. Sleeve 108 is prevented from moving upward
by upper cylinder 100 because flange 110 would make contact with
lower surface 101 of upper sleeve 100. Thus, lower sleeve 108 requires
no attachment devices. A dowel is used to prevent rotation of the
lower sleeve 108.
Piston 82 has two moving seals 114 and 116 to prevent leakage from
hydraulic fluid ring 86. Typical moving seals are polyurethane and
rubber Parker Polypak seals. The range of motion of piston 82 is
240 mm in a preferred embodiment. Lower moving seal 116 is always
disposed between piston 82 and lower sleeve 108. Upper moving seal
116 is always disposed between piston 82 and upper sleeve 100.
Because the oil in hydraulic fluid ring 86 supports the piston
82 and shaft 20 it is under pressure. In a preferred embodiment,
the pressure in hydraulic fluid ring 86 is 300-2000 psi. Therefore,
seals 106 112 114 and 116 are designed to withstand 5000 psi
to prevent leakage from hydraulic fluid ring 86. In a preferred
embodiment, the oil used in hydraulic fluid ring 86 is ISO grade
68.
To install the sleeve and seal system, bearing 80 and piston 82
must be removed from the spider 46. The bearing 80 and piston 82
can be removed through the top of spider 46 after bearing retainer
plate 92 is detached from shaft 20. Once piston 82 and bearing 80
have been removed, the upper cylindrical sleeve 100 and lower cylindrical
sleeve 108 are accessible from the top of spider 46. Bolts 104 of
upper sleeve 100 are removed so that upper sleeve 100 may be removed
through top of spider 46. Lower sleeve 108 may then be lifted out
through top of spider 46.
The present sleeve and seal arrangement has several advantages
over conventional piston sleeves and seals. The first advantage
is top service. The sleeves and seals in the present invention may
be installed through the top of spider 46. This is an advantage
because the area underneath spider 46 is not as accessible for maintenance
and installation purposes. Conventionally, the shaft 20 or spider
46 need to be removed for access. Therefore, top service reduces
the time and cost of maintenance on a gyratory crusher 10. Secondly,
the seal and sleeve arrangement requires fewer parts than conventional
sealing arrangements. There are no separate retainers that must
be bolted in to seal the hydraulic space 86. Upper sleeve 100 and
lower sleeve 108 in combination with o-rings 106 and 112 and moving
seals 114 and 116 seal the hydraulic ring 86 adequately without
additional rings. Thirdly, the present invention does not require
hardware for installation of the lower cylindrical sleeve 108. This
is because the lower sleeve 108 is held captive by upper sleeve
100 and spider 46. This reduction in hardware reduces maintenance
costs.
Gyratory crusher 10 operates as follows. When the drive mechanism
22 is driven by any appropriate means, mechanism 22 transmits power
to the eccentric 24. Eccentric 24 causes the gyration of the head
assembly 26 resulting in the crushing of the material in the crushing
chamber 50. The phantom lines flanking the mantle 34 and shaft 20
axis on FIG. 1 indicate the range of gyratory motion.
While several embodiments of the invention have been described,
it should be apparent to those skilled in the art that what has
been described is considered at present to be the preferred embodiments
of a spider piston sleeve and seal arrangement. However, in accordance
with the patent statutes, changes may be made in the design without
actually departing from the true spirit and scope of this invention.
The following claims are intended to cover all such changes and
modifications which fall within the true spirit and scope of this
invention. |