Abstrict A gyratory crusher with a tramp iron relief system having an annular
manifold is disclosed. The gyratory crusher includes a frame, with
the frame including a circumferential manifold ring having an internal
hydraulic channel. A bonnet and a gyratory head are supported by
the frame, with the gyratory head being spaced relative to the bonnet
such that a crushing chamber is formed therebetween. The bonnet
is adjustably mounted to the frame to permit relative vertical movement
between the bonnet and the gyratory head. A hydraulic relief system
is provided and includes at least one hydraulic cylinder operatively
interconnecting the bonnet and the frame and being in flow communication
with the hydraulic channel. The hydraulic relief system is arranged
to allow uncrushable material to automatically pass through the
crushing chamber.
Claims What is claimed and desired to be secured by Letters Patent is
as follows:
1. A gyratory crusher for crushing material, comprising:
a frame, the frame including a circumferential manifold ring having
an internal hydraulic channel;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head; and
a hydraulic relief system operatively interconnecting the bonnet
and the frame and being in flow communication with the hydraulic
channel, the hydraulic relief system being arranged to allow uncrushable
material to automatically pass through the crushing chamber.
2. The gyratory crusher of claim 1 wherein the hydraulic relief
system includes at least one hydraulic cylinder.
3. The gyratory crusher of claim 2 wherein the hydraulic relief
system includes at least one hydraulic accumulator in flow communication
with the hydraulic cylinder and the hydraulic channel.
4. The gyratory crusher of claim 1 wherein the hydraulic relief
system includes a plurality of hydraulic cylinders in flow communication
with a plurality of hydraulic accumulators, and wherein the manifold
ring includes a plurality of ports operatively connecting the hydraulic
cylinders and the hydraulic accumulators to the hydraulic channel.
5. The gyratory crusher of claim 1 wherein the manifold ring includes
a first annular portion and a second annular portion, at least one
of the first and second annular portions including an annular groove,
such that the internal hydraulic channel is formed between the first
and second annular portions.
6. The gyratory crusher of claim 5 wherein each of the first and
second annular portions includes a groove.
7. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head; and
a hydraulic relief system, the hydraulic relief system including
a circumferential manifold ring attached to and surrounding a portion
of the frame, the manifold ring being adapted to form an internal
hydraulic channel, the hydraulic relief system further including
hydraulic cylinders operatively interconnecting the bonnet and the
frame and being in flow communication with the hydraulic channel;
whereby the hydraulic relief system permits relative displacement
between the bonnet and the frame to permit uncrushable material
to pass through the crushing chamber.
8. The gyratory crusher of claim 7 wherein the hydraulic relief
system includes hydraulic accumulators in flow communication with
the hydraulic cylinders and the hydraulic channel.
9. The gyratory crusher of claim 7 wherein the manifold ring includes
a plurality of ports operatively connecting the hydraulic cylinders
and the hydraulic accumulators to the hydraulic channel.
10. The gyratory crusher of claim 7 wherein the manifold ring
includes a first annular portion and a second annular portion, at
least one of the first and second annular portions including an
annular groove, such that the internal hydraulic channel is formed
between the first and second annular portions.
11. The gyratory crusher of claim 10 wherein each of the first
and second annular portions includes a groove.
12. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
an annular manifold attached to and surrounding a portion of the
frame, a portion of the annular manifold forming an internal hydraulic
channel; and
a hydraulic relief system, the hydraulic relief system including
a hydraulic cylinder operatively interconnecting the bonnet and
the frame and being in flow communication with the annular manifold
hydraulic channel, the hydraulic relief system being adapted to
permit uncrushable material to automatically pass through the crushing
chamber.
13. The gyratory crusher of claim 12 wherein the hydraulic relief
system includes a hydraulic accumulator in flow communication with
the hydraulic cylinder and the hydraulic channel.
14. The gyratory crusher of claim 13 wherein the annular manifold
includes a plurality of ports operatively connecting the hydraulic
cylinder and the hydraulic accumulator to the hydraulic channel.
15. The gyratory crusher of claim 12 wherein the annular manifold
includes a first portion and a second portion, at least one of the
first and second portions including a peripheral groove, such that
the internal hydraulic channel is formed between the first and second
annular portions.
16. The gyratory crusher of claim 15 wherein each of the first
and second annular portions includes a groove.
17. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
a rigid annular manifold integrally formed with and surrounding
a portion of the frame, a portion of the annular manifold defining
an internal hydraulic channel; and
a hydraulic relief system, the hydraulic relief system including
a hydraulic cylinder operatively interconnecting the bonnet and
the frame and being in flow communication with the hydraulic channel,
the hydraulic relief system being arranged to allow uncrushable
material to automatically pass through the crushing chamber.
18. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
a first annular ring being attached to and surrounding a portion
of the frame, a portion of the first annular ring having a peripheral
groove;
a second annular ring rigidly secured to the first annular ring,
the second annular ring being generally concentric with the first
annular ring and enclosing the groove thereby forming an internal
annular hydraulic channel; and
a hydraulic relief system, the hydraulic relief system including
a hydraulic cylinder operatively interconnecting the bonnet and
the frame and being in flow communication with the hydraulic channel;
whereby the hydraulic relief system permits uncrushable material
to automatically pass through the crushing chamber.
19. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
a first annular ring being attached to and surrounding a portion
of the frame;
a second annular ring rigidly secured to the first annular ring,
the second annular ring being generally concentric with the first
annular ring
a groove in at least one of the first and second rings such that
an internal annular hydraulic channel is formed between the first
and second rings; and
a hydraulic relief system operatively interconnecting the bonnet
and the frame and being in flow communication with the hydraulic
channel;
whereby the hydraulic relief system permits uncrushable material
to automatically pass through the crushing chamber.
20. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
an outer wall supported by the frame and surrounding a portion
of the frame;
an annular manifold supported by the frame and surrounding a portion
of the outer wall, the annular manifold including an internal hydraulic
channel; and
a hydraulic relief system, the hydraulic relief system including
a hydraulic cylinder operatively interconnecting the bonnet and
the frame and being in flow communication with the hydraulic channel,
the hydraulic relief system being adapted to permit uncrushable
material to automatically pass through the crushing chamber.
21. A gyratory crusher for crushing material, comprising:
a frame;
a bonnet and a gyratory head supported by the frame, the gyratory
head being spaced relative to the bonnet such that a crushing chamber
is formed therebetween, the bonnet being adjustably mounted to the
frame to permit relative vertical movement between the bonnet and
the gyratory head;
a hydraulic relief system, the hydraulic relief system including
a plurality of hydraulic cylinders operatively interconnecting the
bonnet and the frame;
annular manifold means for defining a hydraulic fluid flow path
about the periphery of the frame, the manifold means being rigidly
defined by a portion of the frame, the manifold means operatively
communicating hydraulic fluid between the plurality of hydraulic
cylinders;
the hydraulic relief system and the manifold means thereby permitting
uncrushable material to automatically pass through the crushing
chamber by allowing relative displacement between the bonnet and
the frame.
Description BACKGROUND OF THE INVENTION
The invention relates generally to a gyratory or cone crusher.
Gyratory crushers or cone crushers are characterized by crushing
heads having a generally cone-shaped outer surface, which are mounted
to undergo gyratory motion. The cone-shaped crushing head of a gyratory
crusher is generally centered about a cone axis that is angularly
offset from a vertical crusher axis generally centered through the
crusher. The outer surface of the head is protected by a replaceable
mantel.
The crushers are further characterized by a bowl-shaped member,
sometimes referred to as a concave or bonnet, disposed in an inverted
position generally over the cone-shaped crushing head and centered
on the vertical crusher axis. The inner surface of the bowl-shaped
member is protected by a replaceable bowl liner. The outer dimensions
of the head and mantel are smaller than the corresponding inner
dimensions of the bowl liner. The head is mounted such that there
is a space between the mantel and the bowl liner, sometimes referred
to as the "crushing chamber" or "crushing cavity".
The volume of the crushing cavity can be increased by altering the
shape of the exposed surface of the bowl liner and/or the shape
of the exposed surface of the mantel. It can also be increased or
decreased by vertically adjusting the separation between the mantel
and the bowl liner. The bowl-shaped member has an upper opening
through which material to be crushed can be fed into the crushing
cavity.
The smallest distance between the mantel and the bowl liner at
the bottom of the crushing cavity is called the "closed side
setting" or "setting" of the crusher. The width of
the setting determines the size of crushed materials operably produced
by the crusher. The setting can be enlarged to increase the size
of the crushed material produced by the crusher, and can be decreased
to reduce the size of the crushed material produced by the crusher.
The setting can be adjusted by simply raising or lowering the elevation
of the bowl liner relative to the elevation of the cone head. The
setting of some cone crushers is adjusted by raising or lowering
the head. The difference between the width of the closed side setting
and the spacing between the mantel and the bowl liner at the bottom
of the crushing cavity directly opposite from the closed side setting,
sometimes called the "open" side or "open side setting",
is called the "throw" or "stroke" of the crusher.
The small angular offset of the cone axis relative to the vertical
crusher axis is provided by mounting the head on an eccentric element,
or other suitable mounting. The head is caused to gyrate relative
to the bowl-shaped member by rotating that mounting or eccentric
element. As the eccentric element rotates, one side of the head
is caused to approach the bowl liner until it attains the closed
side setting while the opposite side of the head recedes from the
bowl liner until it simultaneously attains the open side setting.
The closed side setting and open side setting operably travel around
the periphery of the lower end of the crushing cavity as the eccentric
element is rotated, each making a complete revolution around the
cone head for each revolution on the eccentric element. The magnitude
of the gyration is determined by the angle that the cone axis is
offset from the crusher axis and by the location of the point at
which those two axes most closely approach or intersect.
State-of-the-art gyratory or cone crushers are generally driven
by a horizontally disposed countershaft which radially extends into
a lower part of a generally cylindrical crusher housing. An inner
end of the countershaft is coupled through a pinion and ring gear
to the eccentric element to rotatably drive the eccentric element.
A motor (either electric or combustion) is used to drive the crusher.
The speed of the motor, the size ratio of the pulleys on the motor
and the crusher, and the gearing of the eccentric element determine
the speed at which the head gyrates, sometimes referred to as the
"gyrational speed". The gyrational speed selected for
each crusher depends on the particular application for which the
crusher is to be used. Increasing or decreasing the gyrational speed
is usually a matter of changing the speed of the motor, changing
the relative sizes of the pulleys on the motor and the crusher,
and/or changing the gear ratios for the eccentric.
The gyratory or gyrating motion of the cone-shaped crushing head
performs a material comminution action on material, such as rock,
ore, coal and other hard substances, as the material is fed through
the bowl opening into the crushing cavity. The material typically
moves by gravity through the annular space between the exposed surface
of the stationary bowl liner and the exposed surface of the cone-shaped
mantel. As the gyrating head approaches the liner, it crushes the
material; as it recedes from the liner, the material falls farther
down the crushing cavity to undergo further crushings during subsequent
revolutions of the eccentric member and as the separation between
the bowl liner and the head gradually decreases from top to bottom.
This progressive crushing action repeatedly occurs until the crushed
material is discharged from the bottom of the crushing cavity.
A continuing problem with prior art cone crushers is the provision
of reliable and inexpensive dust seals to prevent dust and grit,
that is invariably generated in abundance during the crushing operation,
from gaining access to critical moving parts. The problem arises
from the need to attach one side of such a seal to a portion of
a crusher that moves relative to another portion of the crusher
to which the other side of the seal must be attached.
Another problem with cone crushers is the external plumbing used
for tramp iron relief systems for automatically processing uncrushable
material through the crushing chamber. The plumbing, being exposed
on the exterior of the crushers, is largely unprotected and prone
to accidental damage and disruption.
A further desirable improvement for a cone crusher would be the
provision of a self-contained lubricating system whereby auxiliary
equipment located externally to the crusher could be eliminated.
A related desirable improvement would be to provide a more reliable
and simpler method of supporting the gyrating head of the crusher
and distributing lubricating oil within the crusher.
Another problem with prior art cone crushers is the thermal stresses
that develop within the lower frameworks of the crushers. The thermal
stresses arise due to the difference in temperature of the working
parts of the crushers during the crushing operation relative to
the temperature of the outer walls of the lower framework. The temperature
difference is acerbated by the crushed material being discharged
against and sliding down the outer walls of the lower framework
thereby cooling those walls, sometimes to a temperature lower than
ambient.
Another desirable improvement for a cone crusher would be to accurately
and precisely locate the eccentric element thereof whereby the drive
assembly associated therewith could be simplified without sacrificing
long-wear characteristics and reliability.
What is needed is a gyratory crusher that has a dust seal that
reliably and inexpensively prevents dust and grit from gaining access
to critical moving parts of the crusher; that has a tramp iron relief
system without external plumbing; that has a self-contained lubricating
system; that has a simpler and more reliable cone head mounting
and supporting system; that has a precisely and accurately located
eccentric element, even during the crushing operating; that allows
simplification of the drive arrangement thereof; that has a thermal
relief system whereby temperature differences between moving parts
of the cone head supporting system and walls of the lower framework
of the crusher are reduced; and that has easily replaceable parts
that minimize maintenance costs.
SUMMARY OF THE INVENTION
An improved gyratory crusher is provided for crushing rock, ore,
coal and other hard substances. The gyratory crusher includes a
lower frame portion, an upper frame portion supported by the lower
frame portion, and a bonnet supported by the upper frame portion.
The bonnet has an upper opening for receiving the material to be
crushed.
The gyratory crusher also includes an eccentric member and a conically
shaped crusher head. The eccentric member is pivotally mounted on
the lower frame portion about a crusher axis spaced centrally and
vertically relative to the lower frame member. The crusher head
is pivotally mounted on the eccentric member about a cone head axis
spaced generally centrally and vertically relative to the lower
frame portion wherein the cone head axis is angularly offset from
the crusher axis and intersects the crusher axis above the crusher
head. A crushing chamber is formed between the crusher head and
the bonnet.
The mounting arrangement of the gyratory crusher also includes
a plurality of hydrostatic bearings for operably supporting the
crusher head, a pair of taper bearings configured to operatively
provide rotational displacement of the eccentric member about the
crusher axis, and a spherical bearing configured to operatively
provide rotational displacement of the crusher head about the cone
head axis. The crusher head is mounted on a main shaft having a
tapped partial bore adapted to threadably receive a mantel stud.
One or more partial bores spaced across the threads of the tapped
partial bore and the threads of the mantel stud are each adapted
to receive a dowel pin as the mantel stud is in threaded engagement
with the tapped partial bore. The dowel pin or pins prevent overtightening
of the self-tightening mantel stud during crushing operations of
the gyratory crusher.
The gyratory crusher also includes a flexible seal that is configured
to operatively protect moving components thereof from dust and grit
generated during crushing operations. An outer edge of the flexible
seal is secured to the crusher head and an inner edge of the flexible
seal is secured to an outer race of a ball bearing seal, the inner
race of which is secured to non-rotating members of the mounting
arrangement.
The gyratory crusher also includes a hydraulic tramp iron relief
system that is configured to automatically allow uncrushable material
to pass through the crushing chamber. The tramp iron relief system
includes channels formed internally within the structure of the
lower frame portion to connect cylinders and accumulators of the
tramp iron relief system in high-pressure hydraulic fluid flow communication.
The gyratory crusher also includes a self-contained lubricating
system configured to operatively lubricate the moving components
and sliding interfaces thereof, and to operably transfer thermal
energy from the moving parts of the mounting arrangement to the
lower frame portion to thereby reduce thermal stress within the
crusher.
A driving arrangement, including a bevel gear centered about the
crusher axis and secured directly to the eccentric member, provides
power for operating the crusher.
PRINCIPAL OBJECTS AND ADVANTAGES OF THE INVENTION
The principal objects and advantages of the present invention include:
providing a gyratory crusher that has a flexible dust seal arrangement;
providing such a gyratory crusher that has a tramp iron relief system
without external plumbing interconnecting cylinders and accumulators
thereof; providing such a gyratory crusher that has a self-contained
lubricating system; providing such a gyratory crusher that has a
hydrostatically supported cone head; providing such a gyratory crusher
that has a precisely and accurately located eccentric element relative
to lower framework of the crusher; providing such a gyratory crusher
that has a drive arrangement attached directly to an eccentric element
of the crusher; providing such a gyratory crusher that has a thermal
relief system whereby thermal energy from moving parts of a cone
head supporting arrangement of the crusher is transferred to a lower
framework of the crusher; providing such a gyratory crusher that
has easily replaceable parts to minimize maintenance costs; and
generally providing such a gyratory crusher that is efficient in
operation, capable of long operating life, and particularly well
adapted for the proposed usages thereof.
Other objects and advantages of this invention will become apparent
from the following description taken in conjunction with the accompanying
drawings wherein are set forth, by way of illustration and example,
certain embodiments of this invention.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a fragmentary, side elevational view of a gyratory crusher
including an elevating arrangement and cylinders and accumulators
of a tramp iron relief system thereof, according to the present
invention.
FIG. 2 is a fragmentary, partially cross-sectional view of the
gyratory crusher, taken along line 2--2 of FIG. 1.
FIG. 3 is an enlarged and fragmentary, side elevational view of
the gyratory crusher, showing one of the plurality of cylinders
of the tramp iron relief system with portions broken away to reveal
details thereof.
FIG. 4 is a further enlarged and fragmentary, side elevational
and cross-sectional view of one of the plurality of cylinders of
the tramp iron relief system of the gyratory crusher, taken along
line 4--4 of FIG. 3.
FIG. 5 is an enlarged and fragmentary, top plan view of one of
the plurality of accumulators of the tramp iron relief system of
the gyratory crusher taken along line 5--5 of FIG. 2 with portions
broken away to reveal details thereof.
FIG. 6 is a fragmentary top plan view of the gyratory crusher taken
along line 6--6 of FIG. 2 with a portion cut away to reveal details
thereof, showing a thermal stress relief arrangement thereof.
FIG. 7 is a further enlarged and fragmentary, partially cross-sectional
and side elevational view of a stop pin arrangement of the gyratory
crusher.
FIG. 8 is an enlarged and fragmentary, partially cross-sectional
and side elevational view of a fluted bowl liner of the gyratory
crusher.
FIG. 9 is a further enlarged and fragmentary, partially cross-sectional
view of the gyratory crusher, showing a mantel stud thereof.
FIG. 10 is a yet further enlarged and fragmentary, partially cross-sectional
view of the gyratory crusher, showing a dust seal arrangement thereof
in the vicinity of a closed side setting of the gyratory crusher.
FIG. 11 is a fragmentary view of the gyratory crusher, similar
to that of FIG. 10 but showing the dust seal arrangement in the
vicinity of an open side setting of the gyratory crusher.
FIG. 12 is a yet further enlarged and fragmentary view of the gyratory
crusher, similar to that of FIG. 10 but showing an alternate dust
seal arrangement.
FIG. 13 is a schematic representation of a lubricating system of
the gyratory crusher, according to the present invention.
FIG. 14 is a fragmentary and further enlarged plan view of the
elevating arrangements of the gyratory crusher.
FIG. 15 is a partial exploded and perspective view of accumulator
attaching means of the gyratory crusher, according to the present
invention.
DETAILED DESCRIPTION OF THE INVENTION
As required, detailed embodiments of the present invention are
disclosed herein; however, it is to be understood that the disclosed
embodiments are merely exemplary of the invention, which may be
embodied in various forms. Therefore, specific structural and functional
details disclosed herein are not to be interpreted as limiting,
but merely as a basis for the claims and as a representative basis
for teaching one skilled in the art to variously employ the present
invention in virtually any appropriately detailed structure.
The reference numeral 1 generally refers to a gyratory crusher
in accordance with the present invention, as shown somewhat simplified
to highlight particular features of the present invention in FIGS.
1 through 15. The crusher 1 includes frame means 3 head mounting
means 5 adjusting means 7 lubricating means 9 thermal stress
relief means 11 dust seal means 13 and a tramp iron relief system
15.
The frame means 3 includes a lower frame portion 21 and an upper
frame portion 23. A "V-seat" arrangement 25 as shown
in FIG. 7 is peripherally situated between the lower frame portion
21 and the upper frame portion 23 similar to that disclosed in
U.S. Pat. No. 4773604 entitled "Seat Member for Gyratory
Rock Crusher Bowls" and issued Sep. 27 1988. A bowl, concave
or bonnet 31 is mounted on the upper frame portion 23 by threads
33. A bowl liner 35 having an exposed surface 37 is replaceably
mounted on the bonnet 31 by liner connectors 39. The bowl liner
35 is a wear item that is replaceable while the crusher 1 is shut
down during maintenance periods. The upper frame portion 23 the
bonnet 31 and the bowl liner 35 which may be collectively referred
to herein as an upper assembly 41 are all centered about a vertically
oriented crusher axis 51 located centrally through the crusher
1. The bowl liner 35 has the general shape of a hollow truncated
pyramid with a generally circularly shaped upper opening 53 and
a wider, generally circularly shaped lower opening 55. The upper
opening 53 provides a material feed or intake opening for the crusher
1.
Partially located within the bowl liner 35 and extending through
the lower opening 55 into the space encompassed by the bowl liner
35 is a crusher head or cone head 61 of the crusher 1. The cone
head 61 is generally conically shaped. A mantel 63 replaceably
mounted on the cone head 61 provides a conical upwardly facing
crushing surface 65 for the cone head 61. The cone head 61 is centered
about a generally vertically oriented cone head axis 67 which is
disposed and supported at an angle of deviation, as indicated by
the numeral 69 in FIG. 2 with respect to the crusher axis 51. The
cone head axis 67 and the crusher axis 51 intersect at an apex of
gyration or apex 71 that lies centrally above the crusher 1. During
the operation of the crusher 1 the cone head 61 gyrates about the
apex 71 with respect to the bonnet 31.
The head mounting means 5 includes a main shaft 81 centered about
the cone head axis 67 for receiving the cone head 61 as shown
in FIG. 2. An upper end 83 of the main shaft 81 has a tapped partial
bore 85 for threadably receiving a mantel stud 87 as shown in FIG.
9.
The mantel stud 87 has an inner threaded portion 89 for mating
with the partial bore 85 and an outer threaded portion 91 for mating
with a mantel nut 93 as hereinafter described. The handedness of
the inner threaded portion 89 and the outer threaded portion 91
is such that the mantel stud 87 and the mantel nut 93 are self-tightening.
The threads of the inner threaded portion 89 and the outer threaded
portion 91 have an appropriate pitch, such as four threads per inch
for the outer threaded portion 91 and six threads per inch for the
inner threaded portion 89.
At least one, preferably two or more, partial bores 95 axially
aligned with the cone head axis 67 are located across the mated
threads of the partial bore 85 and the inner threaded portion 89
for receiving a respective dowel pin 97 therein. The dowel pins
97 are adapted to prevent over-tightening of the mantel stud 87
during the crushing operation and to thereby facilitate subsequent
removal or replacement of the mantel stud 87 thereby allowing low-cost
replacement of a corresponding thread system that holds a mantel
bolt 99 without having to remove or replace the main shaft 81.
The mantel 63 is attached to the cone head 61 by placing the mantel
63 on the cone head 61 and placing a mantel washer or "torch
ring" 111 over the outer threaded portion 91. The mantel nut
93 is threadably advanced along the outer threaded portion 91. The
mantel nut 93 has outwardly tapered shoulders 113 which, in conjunction
with the torch ring 111 and an appropriately sized and shaped orifice
115 through the mantel 63 centers and secures the mantel 63 to
the cone head 61. A mantel cap 117 is secured to the mantel nut
93 by the bolt 99 to protect the mantel nut 93 and the torch ring
111 from material falling through the upper opening 53.
The head mounting means 5 also includes an eccentric member 131
mounted within an encasement portion 133 of the lower frame portion
21. Rotational movement of the eccentric member 131 relative to
the encasement portion 133 is provided by a pair of taper bearings
135 137 centered about the crusher axis 51 as shown in FIG. 11.
A cavity 139 formed within the eccentric member 131 is configured
to provide the angular offset 69. Rotational movement of the cone
head 61 relative to the eccentric member 131 is provided by a spherical
bearing 141 centered about the cone head axis 67. A bushing 143
and a spacer 145 about the main shaft 81 appropriately locate the
spacing of the spherical bearing 141 relative to the main shaft
81. Counterweight 147 can be attached to the eccentric member 311
to balance the gyratory forces, as needed.
To provide adequate mounting for the taper bearings 135 137 while
also providing added support for the substantial stress forces generated
during the crushing operating, the cone head 61 is mounted in abutting
engagement with a plurality of hydrostatic bearings 161 mounted
on thrust seats 163 equidistantly spaced around the crusher axis
51. A bottom surface 165 of the cone head 61 is spherically shaped
with the center of curvature thereof located at the apex 71 whereby
the abutting engagement between the hydrostatic bearings 161 and
the surface 165 form a sliding interface as the cone head 61 gyrates
during the crushing operation.
The thrust seats 163 are mounted on and jointly supported by an
upper side 167 of the encasement portion 133 and the taper bearings
135 137. The primary purpose for partially supporting the cone
head 61 by the taper bearings 135 137 is to "load" the
taper bearings 135 137. In so doing, the eccentric member 131 is
precisely located, both axially and radially, relative to the encasement
portion 133. Selected ones of a plurality of shims 169 having different
thicknesses provide the desired loading of the taper bearings 135
137.
By precisely mounting and locating the eccentric member 131 relative
to the encasement portion 133 with the taper bearings 135 137
a gear 181 such as a spiral bevel gear, can be centered about the
crusher axis 51 and attached directly to the eccentric member 131
thereby eliminating the more complicated, more expensive and higher
maintenance gear arrangements of the prior art arrangements. A drive
train or drive pinion arrangement 183 meshed with the gear 181
and connected to a sheave 185 or other suitable means, provides
means for powering the crusher 1.
The crushing operation is effected by the spacing between the cone
head 61 and the bonnet 31 or, more particularly, the spacing between
the mantel 63 and the bowl liner 35. A releasable clamping arrangement
187 jams the opposing threads 33 against each other to prevent relative
rotation of the threads 33 except when desired. Preferably, the
clamping arrangement 187 is activated by hydraulically operated
by appropriately spaced cylinders 189. Alternately, the clamping
arrangement 187 may be activated by utilizing bolts and nuts 190.
Wear occurring on the respectively exposed mantel surface 65 and
the bowl liner surface 37 tends to increase the spacing therebetween.
Consequently, the adjusting means 7 which provides periodic corrective
adjustments of the spacing between the mantel 63 and the bowl liner
35 includes the threads 33 which permit continuous adjustment of
the axial position of the bonnet 31 in a step-less up or down displacement
by rotating the bonnet 31 about the crusher axis 23 with respect
to the upper frame portion 7 the ring gear 191 and a pair of drive
motors 193 as shown in FIG. 1.
The adjusting means 7 also includes a plurality, four for example,
of vertically oriented cleats 195 secured to a wall 197 of the upper
frame portion 23. The ring gear 191 has a corresponding plurality
of vertically oriented grooves 199. The ring gear 191 cleats 195
and grooves 199 are configured whereby the ring gear 191 can be
displaced vertically alongside the wall 197 but cannot be horizontally
rotated relative to the wall 197 due to interaction between the
cleats 195 and the grooves 199 as shown in FIG. 14.
The drive motors 193 are mounted on the lower frame portion 21.
A plurality of rollers 201 supporting the ring gear 191 are also
mounted on the lower frame portion 21 whereby the ring gear 191
is maintained in gearing engagement with the drive motors 193.
To adjust the separation between the mantel 63 and the bowl liner
35 the hydraulic cylinders 189 are bled whereby the jamming pressure
between the opposing threads 33 is reduced allowing the drive motors
193 to displace the mating surfaces of the threads 33 relative to
each other. Then, the drive motors 193 are activated whereby the
ring gear 191 is horizontally rotated. If it is desired to increase
the separation between the bowl liner 35 and the mantel 63 the
drive motors 193 are operated in unison to cause the upper frame
portion 23 to be threadably advanced upwardly. Conversely, if it
is desired to decrease the separation between the bowl liner 35
and the mantel 63 the drive motors 193 are operated in unison in
the opposite direction to cause the upper frame portion 23 to be
threadably advanced downwardly. After attaining the desired separation
between the bowl liner 35 and the mantel 63 forces exerted by the
clamping arrangement 187 are increased to maintain the newly established
separation.
Included conical angles of the bowl liner 35 and the mantel 63
are configured to provide an annular space or crushing chamber 211
between the bowl liner surface 37 and the mantel surface 65 the
width thereof generally decreasing downwardly. An annular gap 213
at the lower opening 55 between the bowl liner 35 and the mantel
63 constitutes an annular material discharge opening 215 from the
crushing chamber 211. During operation of the crusher 1 material
is fed into the crushing chamber 211 through the upper opening 53
which material is gravitationally urged downwardly through the annular
crushing chamber 211 and is reduced in size through repeated crushing
contacts between the adjacent surfaces 37 and 65 of the bowl liner
35 and the mantel 63.
The maximum size of material that can be crushed by the crusher
1 is determined by the spacing between the uppermost ends of the
bowl liner surface 37 and the mantel surface 65 as indicated by
the phantom circle designated by the numeral 217 in FIG. 8. If desired,
a plurality of flutes 219 may be formed in the bowl liner surface
37 as shown in FIG. 8 whereby occasional oversized material may
be received by the crushing chamber 211 to thereby increase the
maximum opening of the crushing chamber 211 without increasing the
size of the crusher 1.
The lubricating means 9 of the crusher 1 is self-contained and
includes a first pumping arrangement 231 for circulating oil through
the crusher 1 for lubricating the various moving parts thereof.
Oil for the first pumping arrangement 231 is contained in an oil
pan 233. The first pumping arrangement 231 as schematically illustrated
in FIG. 13 draws oil from the oil pan 233 by a lubricating portion
235 of a pump 237 and directs that oil by an oil line 239 through
a high-pressure filter 241 a pressure transducer 243 and a flow
divider 245. If a failure should occur whereby oil pressure should
unexpectedly drop at the pressure transducer 243 such as a broken
oil line, the pressure transducer 243 is adapted to signal shut-down
controls 247 which immediately shut-down operation of the crusher
1. If, instead, oil pressure in the oil line 239 should exceed a
certain pre-determined level, oil will be bled from the oil line
239 by a relief valve 249 and routed back to the oil pan 233.
The flow divider 245 distributes oil flowing therethrough separately
to each of the hydrostatic thrust bearings 161 and to the drive
pinion arrangement 183 from where the oil gravitationally returns
to the oil pan 233 as indicated by the arrow designated by the
numeral 251 in FIG. 13. The flow divider 245 also distributes oil
to the drive train 183 as indicated by the dashed line designated
by the numeral 252.
Monitoring means 253 monitors the volume of oil being processed
through the flow divider 245. If oil flow to the hydrostatic thrust
bearings 161 or the drive pinion arrangement 183 as evidenced by
a reduction in volume of oil flow therethrough as determined by
the monitoring means 253 the monitoring means 253 will signal the
shut-down controls 247 to immediately shut-down operation of the
crusher 1.
Pressurized oil is conveyed from the flow divider 245 to the interface
between the hydrostatic bearings 161 and the bottom surface 165
of the cone head 61 by oil channels 255 for lubrication purposes.
The oil is sufficiently pressurized whereby the cone head 61 is
slightly elevated and supported on a thin film of oil on each of
the hydrostatic bearings 161. Oil sprays outwardly from the interface
between the hydrostatic bearings 161 and the bottom surface 165
of the cone head 61 and, as it cascades downwardly, lubricates the
other moving parts of the head mounting means 5 therebelow. Spring
loaded wiper rings 257 cause oil sprayed radially outwardly from
the hydrostatic bearings 161 to be directly downwardly onto a seal
bearing 259. Weep holes 261 drain oil from the seal bearing 259
and other pockets for gravitational return to the oil pan 233.
The thermal stress relief means 11 is also self-contained and includes
a second pumping arrangement 281. The second pumping arrangement
281 draws oil from the oil pan 233 by a cooling portion 283 of the
pump 237 and directs that oil through oil line 285 and a filter
287. If the oil temperature should be lower than a pre-determined
temperature, a bypass valve 289 diverts the oil from the oil line
285 to the oil pan 233. When the oil in oil line 285 reaches or
exceeds that pre-determined temperature, oil is no longer diverted
by the bypass valve 289 but, instead, is directed through half-collars
291 abutting a wall 293 of the lower frame portion 21 and into the
oil pan 233. The half collars 291 as shown in FIG. 6 and the oil
circulated therethrough are adapted to elevate the temperature of
the wall 293 to a temperature more closely approximately the temperatures
in the head mounting means 5 to reduce thermal stresses within the
lower frame portion 21 of the crusher 1.
Actually, the thermal relief means 11 serves a dual purpose. In
addition to relieving the thermal stress, the thermal relief means
11 also serves as a cooling means for the lubricating oil.
The dust seal means 13 is adapted to isolate inner moving components,
such as the interface between the hydrostatic bearings 161 and the
bearings 135 137 and 141 from abrasive contamination arising from
the ubiquitous dust and grit generated during the crushing process.
The dust seal means 13 includes a flexible seal 301 having an outer
edge 303 secured to a lower extremity 305 of the cone head 61 and
an inner edge 307 secured to an outer race 309 of the seal 259
an inner race 311 of which is secured to the thrust seats 163. Bearing
balls 312 are captured between the inner race 311 and the outer
race 309 in peripheral grooves thereof.
To provide the flexibility needed to compensate for the oscillatory
displacement of the cone head 61 due to the gyratory motion thereof,
the flexible seal 301 generally has a single-wall construction with
a corrugation-like cross-sectional configuration, as shown in FIG.
10. As the separation between the mantel 63 and the bowl liner 35
at a particular point along the gap 213 approaches the closed side
setting, the corrugations or fingers 313 widen to compensate for
the corresponding increasing separation between the lower extremity
305 and the seal bearing 301. Similarly, as the separation between
the mantel 63 and the bowl liner 35 approaches the open side setting,
the fingers 313 become narrower to compensate for the corresponding
decreasing separation between the lower extremity 305 and the seal
bearing 301.
To compensate for rotation of the cone head 61 relative to the
bowl liner 35 during a crushing operation, the outer race 309 rotates
with the cone head 61 peripherally relative to the inner race 311.
Alternatively, the dust seal means 13 may include a flexible seal
321 having a double-wall construction that forms a bladder 323 therebetween,
as shown in FIG. 12. For some applications, it may be desirable
to pressurize the bladder 323 such as between one to five pounds
per square inch.
The tramp iron relief system 15 includes a lower radial member
331 secured to and spaced radially outwardly from an upper end 333
of the wall 293 of the lower frame portion 21. A peripheral groove
335 is formed in an outer edge 337 of the lower radial member 331.
A plurality of equidistantly spaced partial bores 341 extend radially
inwardly from the groove 335 as shown in FIG. 2. For example, the
tramp iron relief system 15 may include eight of the partial bores
341.
In addition, a port 343 is provided from each of the partial bores
341 through a lower surface 345 of the lower radial member 331
as shown in FIG. 3. The ports 343 are spaced outwardly from the
wall 293 whereby a cylinder 347 can be connected to and suspended
downwardly from a respective one of each of the ports 343. If desired,
the cylinders 347 may be connected to the ports 343 by inserts 349
as shown in FIG. 3 preferably constructed of a dissimilar metal,
such as brass or other suitable material to minimize or eliminate
galling when removing the cylinders 347 from the ports 343. The
cylinders 347 are spaced in close proximity to the wall 293.
The tramp iron relief system 15 also includes a skirt 351 secured
to the lower radial member 331 as shown in FIG. 4. The skirt 351
extends downwardly from the lower radial member 331 to provide some
protection for the cylinders 347. If desired, a groove 353 may be
provided along an inner peripheral surface of the skirt 351 to complement
and provide greater flow capacity for hydraulic fluid being conveyed
along the groove 335.
A piston rod 355 extends downwardly from each of the cylinders
347 and connects to a respective one of a plurality of rocker arm
arrangements 357. Each of the rocker arm arrangements 357 has an
extension 359 extending through a respective one of a plurality
of guides 361. A pair of opposing pull rods 371 extend upwardly
from each end of a respective one of the rocker arm arrangements
357 through corresponding openings 373 in the lower radial member
331 and through additional corresponding openings 375 in an upper
radial member 377 secured to and spaced radially outwardly from
the wall 197 of the upper frame portion 23. Split keepers 379 connected
to upper ends of each of the pull rods 371 provide means for hydraulically
providing substantial hold-down forces between the upper frame portion
23 and the lower frame portion 21.
The tramp iron relief system 15 also includes a plurality of accumulators
385. For example, the crusher 1 may have one of the accumulators
385 positioned in every other space between the cylinders 347. Each
of the accumulators 385 are connected in flow communication with
the groove 335 similarly to that provided by the ports 343 and
the partial bores 341 for the cylinders 347 and, preferably, by
inserts similar to the inserts 349. An appropriately spaced input
port 387 is provided for injecting hydraulic fluid into the tramp
iron relief system 15 from an external hydraulic source 388 as
schematically shown in FIG. 1.
Each of the accumulators 385 are affixed to the wall 293 by accumulator
attaching means, comprising a pair of opposing locators 389 and
an interconnecting hanger 391. Each of the locators 389 is spaced
outwardly from the wall 293 by standoffs 392. The locators have
a pair of slots in a base 393 thereof that allows a cylindrical
edge 394 thereof to be placed and affixed in abutting engagement
with the respective accumulator 385 as shown in FIGS. 5 and 15.
The hanger 391 has a threaded connector 395 at each end thereof
to clamp the accumulator 385 against the cylindrical edges 394.
One of the distinct advantages provided by the present invention
is the elimination of all external plumbing of a hydraulic system
for tramp iron relief purposes.
In an application of the present invention, hydraulic fluid is
injected into the system to pressurize the hydraulics of the tramp
iron relief system 15 to a selected pressure; for example, 2000-2400
psi or other suitable pressure as appropriate to clamp the upper
frame portion 23 to the lower frame portion 21 particularly across
the V-seat arrangement 25.
The closed side setting is adjusted by displacing the bowl liner
35 upwardly or downwardly as needed by clockwise or counterclockwise
rotation of the elevating ring gear 191 as appropriate. The first
pumping arrangement 231 is activated to provide lubricating oil
to the hydrostatic thrust bearings 161 and the drive pinion arrangement
183. The second pumping arrangement 281 is activated to provide
oil to the half collars 291 after the oil reaches or surpasses a
pre-determined temperature. A prime mover 397 as schematically
indicated in FIG. 2 is drivingly engaged with the sheave 185 to
initiate gyration of the cone head 61 relative to the bowl liner
35.
Rock, ores or other material are dropped through the upper opening
53 of the bowl liner 35 and are crushed between the mantel 63 and
the bowl liner 35 as the material being crushed is gravitationally
urged through the crushing chamber 211 to be discharged through
the gap 213 thereof. As the crushing operation progresses, the temperature
of the oil increases until the pre-determined temperature setting
of the bypass valve 289 is reached or exceeded. Then, the bypass
valve 289 directs the oil passing through the second pumping arrangement
281 to and through the half collars 291.
The trajectory of crushed material being discharged from the gap
213 which is generally much cooler than the oil, bearings and other
moving parts of the crusher 1 causes the crushed material to impact
with the wall 293 thereby cooling the wall 293. Due to the temperature
difference between the cooled wall 293 and that of the moving components
of the crusher 1 prior art crushers endure thermal stresses in
addition to the substantial physical stresses inherent in the crushing
process. In the present invention, however, the oil circulated through
the half collars 291 warms the wall 293 thereby counteracting the
cooling effect of the crushed material impacting with the wall 293.
As a result, thermal stresses in the crusher 1 of the present invention
are substantially reduced from those of prior art crushers.
As non-crushable material that is too large to be processed through
the crushing chamber 211 sometimes referred to as "tramp iron",
is dropped into the crushing chamber 211 a portion of the bowl
liner 35 and the association portion of the upper frame portion
23 are forced upwardly from the cone head 61 causing the corresponding
portion of the V-seat arrangement 25 to separate. As the upper frame
portion 23 is forced upwardly, corresponding ones of the pull rods
371 which are secured to the upper radial member 377 by the split
keepers 379 and the rods 355 connected to the pull rods 371 by
the rocker arm arrangements 357 are also forced upwardly.
As the rods 355 are forced upwardly, pistons 399 push hydraulic
fluid thereabove into the enclosed peripheral groove 335. The hydraulic
fluid flows along the groove 335 to each of the plurality of accumulators
385 connected in flow communication with the groove 335. As the
added pressure in the hydraulic fluid is conveyed to the accumulators
385 compressed bladders 401 within the accumulators 385 are further
compressed to temporarily store the added mechanical energy caused
by the tramp iron passing through the crushing chamber 211.
Immediately after the tramp iron has worked its way through the
crushing chamber 211 and dropped from the gap 213 thereby relieving
the upwardly thrusting forces previously exerted by the tramp iron,
the extra pressure stored in the bladders 401 is dissipated as the
upper frame portion 23 which was forced upwardly, returns to its
rest position about the V-seat arrangement 25 also returning the
pistons 399 the piston rods 355 the rocker arm arrangements 357
and the pull rods 371 to their rest positions. As the V-seat arrangement
25 is disturbed, such as during passage of tramp iron or "bowl
float", stop pins 403 prevent rotation of the upper frame portion
23 relative to the lower frame portion 21. Sleeves or inserts 405
are readily removable to facilitate replacement of worn parts interacting
with the stop pins 403 and of the pins 403 themselves to thereby
minimize maintenance costs.
It is to be understood that while certain forms of the present
invention have been illustrated and described herein, it is not
to be limited to the specific forms or arrangement of parts described
and shown. |