Abstrict A gyratory crusher having a positive head hold-down mechanism.
The crusher includes a frame structure; a first mounting arrangement
including a pair of taper bearings for rotatably mounting an eccentric
member to the frame structure about a vertically oriented first
axis; a second mounting arrangement including a spherical bearing
for spiderlessly and rotatably mounting a main shaft to the eccentric
member about a substantially vertically oriented second axis angularly
offset from the first axis; a crusher head mounted on said main
shaft; drive means including a bevel gear secured to the eccentric
member and a drive pinion arrangement for rotating said eccentric
member about the first axis; a hold-down mechanism fixedly mounted
to the crusher head for preventing vertical displacement of the
crusher head relative to the a plurality of hydrostatic bearings
operably supporting the crusher head; and seal means for protecting
moving components of the crusher.
Claims What is claimed and desired to be secured by Letters Patent is
as follows:
1. A gyratory crusher for crushing material, comprising:
(a) a frame structure;
(b) an eccentric member having a first mounting arrangement configured
to rotatably mount said eccentric member to said frame structure
about a vertically oriented first axis;
(c) a main shaft having a second mounting arrangement configured
to spiderlessly and rotatably mount said main shaft to said eccentric
member about a substantially vertically oriented second axis angularly
offset from said first axis;
(d) a crusher head mounted to said main shaft about said second
axis;
(e) drive means for rotating said eccentric member about said first
axis; and
(f) hold-down means for operably preventing vertical displacement
of said crusher head relative to said eccentric member.
2. The gyratory crusher according to claim 1 wherein said first
mounting arrangement includes a pair of taper bearings.
3. The gyratory crusher according to claim 1 wherein said second
mounting arrangement includes a spherical bearing.
4. The gyratory crusher according to claim 1 wherein said drive
means includes a bevel gear centered about said first axis and secured
to said eccentric member and a drive pinion arrangement enmeshed
with said bevel gear.
5. The gyratory crusher according to claim 1 including:
(a) said frame structure having a lower portion; and
(b) a plurality of hydrostatic bearings mounted on said lower portion
and configured to operably abuttingly engage said crusher head.
6. The gyratory crusher according to claim 5 wherein said hold-down
means is also configured to prevent said crusher head from operably
levitating from said abutting engagement with said plurality of
hydrostatic bearings.
7. The gyratory crusher according to claim 5 wherein said plurality
of hydrostatic bearings are mounted such that said eccentric member
is prevented from vertical displacement relative to said lower portion.
8. The gyratory crusher according to claim 5 including seal means
for operably protecting said first and second mounting arrangements
and said plurality of hydrostatic bearings.
9. The gyratory crusher according to claim 8 wherein said seal
means includes:
(a) a seal bearing having
(1) an inner race connected to said lower portion,
(2) an outer race, and
(3) bearing balls captured between said inner and outer races;
and
(b) a flexible member connected between said crusher head and said
outer race.
10. The gyratory crusher according to claim 1 wherein said hold-down
means includes:
(a) a retaining cup extending beneath said second mounting arrangement
and said main shaft; and
(b) securing means for securing said retaining cup to said main
shaft.
11. The gyratory crusher according to claim 10 wherein said securing
means is rotationally fixed relative to said crusher head.
12. The gyratory crusher according to claim 10 wherein said securing
means includes:
(a) said retaining cup having a centrally situated orifice;
(b) said main shaft having an axially situated throughbore;
(c) a draw rod having a threaded distal end; and
(d) a tapped sleeve mounted in said orifice and configured to threadably
receive said threaded distal end as said draw rod extends through
said axially situated throughbore of said main shaft.
13. The gyratory crusher according to claim 12 wherein said draw
rod has a rod head that is accessible through an upper end of said
throughbore.
14. The gyratory crusher according to claim 13 wherein said securing
means also includes:
(a) said throughbore having a shoulder; and
(b) Belleville-type washers mounted between said rod head and said
shoulder.
15. The gyratory crusher according to claim 13 including a depression
in said rod head configured to matingly receive an Allen wrench.
16. The gyratory crusher according to claim 12 including:
(a) a fitting mounted to said sleeve such that axial and rotational
displacement of said sleeve relative to said fitting is prevented.
17. The gyratory crusher according to claim 12 including a thrust
bearing configured to rotationally mount said tapped sleeve to said
retaining cup about said second axis.
18. The gyratory crusher according to claim 12 including a capture
mechanism configured to operably prevent rotational displacement
of said draw rod relative to said main shaft.
19. The gyratory crusher according to claim 12 including a stop
mechanism configured to provide a reference for repositioning of
said draw rod relative to said tapped sleeve.
20. A gyratory crusher for crushing material, comprising:
(a) a lower frame;
(b) an upper frame supported by the lower frame and having a bonnet
secured thereto, the bonnet having an upper opening for receiving
the material;
(c) an eccentric member rotatably mounted to the lower frame;
(d) a crusher head having a main shaft rotatably mounted to the
eccentric member, the crusher head and the bonnet forming a crushing
chamber therebetween, the main shaft having an upper end and a lower
end;
(e) a drive motor for rotating the eccentric member; and
(f) a hold down assembly coupled to the lower end of the main shaft
arid engaging the eccentric member, the hold down assembly being
adapted to limit axial movement of the main shaft relative to the
eccentric member.
21. The crusher of claim 20 wherein the crusher head main shaft
includes a bore extending axially therethrough, the hold down assembly
including a retaining member and a draw rod, the retaining member
operatively engaging the eccentric member, the draw rod being disposed
through the bore and engaging the retaining member.
22. The crusher of claim 21 wherein the draw rod includes an upper
end having a bolt head secured adjacent the main shaft upper end
by a resilient washer.
23. The crusher of claim 21 wherein the bore includes a lower
end having a counterbore, and wherein a portion of the hold down
assembly is received within the counterbore.
24. The crusher of claim 23 wherein the counterbore and the hold
down assembly portion are conically shaped.
25. The crusher of claim 20 wherein the hold down assembly includes
a retaining cup and a sleeve engaging the retaining cup, the retaining
cup engaging the eccentric member, the sleeve being rotatable relative
to the retaining cup.
26. The crusher of claim 24 wherein the sleeve is mounted to the
retaining cup by thrust bearings.
27. The crusher of claim 25 wherein the sleeve includes a detent,
and wherein the main shaft includes a bore extending axially therethrough
and a draw rod disposed through the bore and engaging the shaft
and the retaining cup, and further wherein the main shaft lower
end includes a retractable member positioned to engage the detent
to thereby prevent rotation of the draw rod and the sleeve relative
to the main shaft.
28. The crusher of claim 27 wherein the retractable member is
spring loaded and retracts along a path generally perpendicular
to the axis of the main shaft.
29. The crusher of claim 27 wherein the retractable member is
removably secured to the main shaft lower end by bolts.
30. The crusher of claim 25 wherein the main shaft includes a
bore extending axially therethrough and a draw rod disposed through
the bore and engaging the shaft and the retaining cup, a portion
of the draw rod being threaded, and further wherein the sleeve includes
a threaded bore sized to receive the draw rod threaded portion,
and further including a lock nut engaging the draw rod threaded
portion for preventing rotation of the sleeve relative to the draw
rod.
31. The crusher of claim 30 wherein the draw rod includes adjustment
indicia imprinted thereon.
32. The crusher of claim 20 wherein the hold down member includes
a tapped sleeve, and the draw rod includes a threaded lower end
engaging the tapped sleeve, and a lock nut for locking the relative
rotational position of the draw rod and to the tapped sleeve.
33. A gyratory crusher for crushing material, comprising:
(a) a frame;
(b) a bonnet;
(c) a gyrating crusher head having a main shaft supported by the
frame for relative gyrational movement, the crusher head and the
bonnet forming a crushing chamber therebetween, the main shaft having
an upper end and a lower end;
(d) a drive motor for gyrating the crusher head; and
(e) a hold down mechanism operatively connecting the lower end
of the main shaft to the frame to prevent axial movement of the
main shaft relative to the frame.
34. The crusher of claim 33 wherein the main shaft includes a
bore extending axially therethrough, the hold down mechanism including
a draw rod disposed through the bore and further including a retaining
cup operatively engaging the frame, a portion of the draw rod engaging
the retaining cup.
35. The crusher of claim 34 wherein the bore includes a lower
end having a counterbore, and wherein the hold down mechanism includes
a sleeve received within the counterbore.
36. The crusher of claim 35 wherein the sleeve includes a detent,
and the main shaft lower end includes a retractable member positioned
to engage the detent to thereby prevent rotation of the draw rod
and the sleeve relative to the main shaft.
37. The crusher of claim 37 wherein the retractable member is
spring loaded and retracts along a path generally perpendicular
to the axis of the main shaft.
38. The crusher of claim 37 wherein the retractable member is
removably secured to the main shaft lower end by bolts.
39. The crusher of claim 35 wherein the counterbore and the sleeve
are conically shaped.
40. The crusher of claim 34 including a sleeve member rotatably
mounted to the retaining cup and engaging the draw rod.
41. The crusher of claim 40 wherein the sleeve member is mounted
to the retaining cup by thrust bearings.
42. The crusher of claim 34 wherein the hold down mechanism includes
a tapped sleeve and the draw rod lower end includes a threaded portion
engaging the tapped sleeve, the tapped sleeve being rotationally
mounted to the retaining cup by thrust bearings.
43. The crusher of claim 34 wherein the draw rod includes an upper
end, the draw rod upper end being secured to the main shaft by a
resilient member.
44. The crusher of claim 33 wherein the main shaft is mounted
to an eccentric member, the eccentric member being rotatably mounted
to the frame.
45. The crusher of claim 33 wherein the hold down mechanism resiliently
engages an upper portion of the main shaft.
46. A device for preventing levitation of a crusher head on a gyratory
crusher, the gyratory crusher having a frame, a bonnet, and a main
shaft supporting the crusher head, a lower end of the main shaft
being received in an eccentric member, the device comprising:
a bore extending axially through the main shaft and having a lower
end;
a draw rod secured to the crusher head and having a lower end extending
to the main shaft lower end;
a sleeve engaging the draw rod lower end; and
a retaining member engaging the sleeve and being operatively connected
to the eccentric member;
whereby the draw rod, the sleeve, and the retaining member cooperate
to prevent undesired vertical movement of the main shaft relative
to the frame.
47. A gyratory crusher comprising a frame, a bonnet, a gyrating
crusher head supported on a main shaft, and a hold down assembly
engaging the main shaft from a lower end thereof to prevent undesired
vertical movement of the crusher head relative to the frame and
further to permit rotational movement of the crusher head relative
to the frame.
Description BACKGROUND OF THE INVENTION
1. Field of the Invention
The invention relates generally to a gyratory or cone crusher.
2. Background of the Related Art
Gyratory crushers or cone crushers are characterized by crushing
or crusher heads having a generally cone-shaped outer surface, which
are mounted to undergo gyratory motion. The cone-shaped crusher
head of a gyratory crusher is generally centered about a head axis
that is angularly offset from a vertical crusher axis generally
centered through the crusher. The outer surface of the head is generally
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 crusher head and centered
about 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 elevation of the mantel relative
to the elevation of 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 crusher head,
or by raising or lowering the elevation of the crusher head relative
to the elevation of the bowl liner. 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 head 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
crusher head for each revolution of the eccentric element. The magnitude
of the gyration is determined by the angle that the head 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/or the crusher,
and/or changing the gear ratios for the eccentric.
The gyratory or gyrating motion of the cone-shaped crusher 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 or crushing cavity 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.
As the separation between the bowl liner and the head gradually
decreases from top to bottom, such progressive crushing action repeatedly
occurs until the crushed material is discharged from the bottom
of the crushing cavity.
The crushing heads of prior art gyratory crushers generally utilize
two different mounting mechanisms--spider-type, wherein head mounting
support is provided both above and below the crushing head, and
spiderless, wherein head mounting support is provided only from
below the crushing head. Obviously, greater demands are placed on
a spiderless mounting mechanism due to the moments randomly generated
during crushing processes.
Further and due to their massiveness, spiderless crushing heads
are generally held in place gravitationally on its underlying mounting
mechanism. During high speed operations, however, the crushing head
tends to levitate or "de-seat", which occurs as the radial
acceleration force exceeds the gravitational component of the crushing
head weight that normally maintains the crushing head seated on
its mounting mechanism. Obviously, the downwardly directed forces
generated during actual crushing operations is more than sufficient
to prevent the crushing head from levitating; the problem arises
primarily during startup or when the crusher has temporarily emptied
between inputs of material to be crushed. Unfortunately, levitation
of a crushing head that is supported by bearings radially displaced
from the longitudinal axis of the crushing head, particularly during
high performance crushing operations, substantially increases wear
and maintenance over that observed for such crushers that do not
experience levitation.
What is needed is a gyratory crusher that has a mechanism for positively
preventing the crushing head from levitating from support bearings
radially displaced from a longitudinal axis thereof.
SUMMARY OF THE INVENTION
An improved gyratory crusher having a positive head hold-down mechanism
is provided for crushing rock, ore, coal and other hard substances.
The gyratory crusher includes a frame structure, including 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, a main
shaft, and a conically shaped crusher head. A first mounting arrangement,
including a pair of taper bearings, is provided for mounting the
eccentric member to the frame structure such that the eccentric
member is rotatable about a vertically oriented crusher axis. A
second mounting arrangement, including a spherical bearing, is provided
for spiderlessly mounting the main shaft to the eccentric member
such that the main shaft is rotatable about a substantially vertically
oriented head axis angularly offset from the crusher axis. The crusher
head is securely mounted on the main shaft such that the crusher
head is rotatable about the head axis and such that a crushing chamber
is formed between the crusher head and the bonnet. The gyratory
crusher also includes a plurality of hydrostatic bearings configured
to operably abuttingly engage and support the crusher head on a
lubricant film provided by a lubricating system configured to operatively
lubricate the moving components and sliding interfaces of the crusher.
The gyratory crusher also includes a hold-down mechanism for preventing
operable vertical displacement and levitation of the crusher head
relative to the the eccentric member and the plurality of hydrostatic
bearings. The hold-down mechanism includes a plate extending beneath
the second mounting arrangement and the main shaft and securing
means for securing the plate to the main shaft. The main shaft has
an axially situated second throughbore such that an elongate draw
rod therethrough threadably and rotationally connects the plate
to the main shaft and the crusher head. The second throughbore is
configured such that the head of the bolt is accessible through
an upper end of the second throughbore.
The gyratory crusher also includes a flexible seal that is configured
to operatively protect moving components thereof, including the
first and second mounting arrangements and the plurality of hydrostatic
bearings, 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.
A driving arrangement, including a bevel gear centered about the
crusher axis and secured 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 precisely and accurately
located eccentric element relative to lower framework of the crusher;
providing such a gyratory crusher that has a positive head hold-down
mechanism; providing such a gyratory crusher having a hold-down
mechanism that prevents operable vertical displacement between a
crusher head and an eccentric member thereof; providing such a gyratory
crusher having a hold-down mechanism that prevents a crusher head
from levitating during use thereof; providing such a gyratory crusher
having a hold-down mechanism that operably maintains a crusher head
and a plurality of hydrostatic bearings thereof in abutting engagement;
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, partially cross-sectional, partially schematic,
side elevational view of a gyratory crusher having a positive head
hold-down mechanism, according to the present invention.
FIG. 2 is an enlarged and fragmentary, partially cross-sectional
and side elevational view of the gyratory crusher having a positive
head hold-down mechanism.
FIG. 3 is a further enlarged and fragmentary, cross-sectional and
side elevational view of a capture mechanism of the gyratory crusher
having a positive head hold-down mechanism, 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 3. The crusher 1 includes frame structure 3 head mounting
means 5 adjusting means 7 lubricating means 9 head hold-down
means 11 dust seal means 13 and a tramp iron relief system 15.
The frame structure 3 includes a lower frame portion 21 having
a wall 23 and an upper frame portion 25 having a wall 27. A "V-seat"
arrangement 29 is peripherally situated between the lower frame
portion 21 and the upper frame portion 25 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 25 by threads
33 thereof mating with threads 34 of the upper frame portion 25.
A bowl liner 35 having an exposed surface 37 is replaceably mounted
on the bonnet 31 by liner connectors 39 by methods known by those
with skill in the art.
The bowl liner 35 is a wear item that is replaceable while the
crusher 1 is shut down during a maintenance procedure. The upper
frame portion 25 the bonnet 31 and the bowl liner 35 which may
sometimes be collectively referred to herein as an upper assembly
41 are all generally centered about a vertically oriented crusher
axis 47 located generally centrally of the crusher 1. The bowl
liner 35 has the general profile of a hollow truncated cone with
a generally circularly shaped upper opening 49 and a wider, generally
circularly shaped lower opening 51. The upper opening 49 provides
a material feed or intake opening for the crusher 1.
Extending upwardly through the lower opening 51 and into the space
encompassed by the bowl liner 35 is a crusher head or cone head
53 of the crusher 1. The crusher head 53 is generally conically
shaped. A mantel 55 replaceably mounted on the crusher head 53
as hereinafter described, provides a conical upwardly facing crushing
surface 57 for the crusher head 53. The crusher head 53 is centered
about a generally vertically oriented head axis 59 which is disposed
and supported at an angle of deviation or angular offset with respect
to the crusher axis 47 as indicated by the numeral 61. The head
axis 59 and the crusher axis 47 intersect at an apex of gyration
or apex 63 that generally lies centrally above the crusher head
53. During operation of the crusher 1 the crusher head 53 gyrates
about the apex 63 with respect to the bonnet 31.
The head mounting means 5 includes a main shaft 69 centered about
the head axis 59 for receiving the crusher head 53 thereon. An
upper end 71 of the main shaft 69 has a tapped partial bore 73 for
threadably receiving a mantel stud 75. It should be noted that the
main shaft 69 and the crusher head 53 are spiderlessly mounted in
the crusher 1.
The mantel stud 75 has an inner threaded portion 77 for mating
with the tapped partial bore 73 and an outer threaded portion 79
for mating with a mantel nut 81 as hereinafter described. The handedness
of the inner threaded portion 77 and the outer threaded portion
79 is such that the mantel stud 75 and the mantel nut 81 are self-tightening.
The threads of the inner threaded portion 77 and the outer threaded
portion 79 have an appropriate pitch, such as four threads per inch
for the outer threaded portion 79 and six threads per inch for the
inner threaded portion 77 for example.
At least one, preferably two or more, partial bores 83 aligned
parallel with the head axis 59 are located across the mated threads
of the partial bore 73 and the inner threaded portion 77 for receiving
a respective dowel pin 85 therein. The dowel pins 85 are adapted
to prevent over-tightening of the mantel stud 75 during the crushing
operations and to thereby facilitate subsequent removal or replacement
of the mantel stud 75 thereby allowing low-cost replacement of
a corresponding thread system that holds a mantel bolt 87 without
having to remove or replace the main shaft 69 or to gain access
to the head hold-down means 11 as hereinafter described.
The mantel 55 is attached to the crusher head 53 by placing the
mantel 55 on the crusher head 53 and positioning a mantel washer
or "torch ring" 89 over the outer threaded portion 79.
The mantel nut 81 which is configured to be threadably advanceable
along the outer threaded portion 79 has outwardly tapered shoulders
91 which, in conjunction with the mantel washer 89 and an appropriately
sized and shaped mantel orifice 93 through the mantel 55 centers
and secures the mantel 55 to the crusher head 53. A mantel cap 95
is secured to the mantel nut 81 by the bolt 87 to protect the mantel
nut 81 and the mantel washer 89 from material falling through the
upper opening 49.
The head mounting means 5 also includes an eccentric member 101
mounted within an encasement portion 103 of the lower frame portion
21. Rotational movement of the eccentric member 101 relative to
the encasement portion 103 is provided by a first or eccentric mounting
arrangement 105 such as a pair of opposing taper bearings 107
109 centered about the crusher axis 47.
The eccentric member 101 in combination with a cavity 111 centered
about the crusher axis 47 within the encasement portion 103 is
configured to provide the angular offset 61. Rotational movement
of the crusher head 53 relative to the eccentric member 101 is provided
by a second or shaft mounting arrangement 113 such as a spherical
bearing 115 with an inside race centered about the head axis 59.
A bushing 119 and a spacer 121 about the main shaft 69 appropriately
locate the spacing of the main shaft 69 relative to the inner race
of the spherical bearing 115. Counterweight 123 can be attached
to the eccentric member 101 to balance the gyratory forces, as shown
in FIG. 1 and/or to the outer race of the spherical bearing 115
as needed.
To provide adequate mounting for the taper bearings 107 109 while
also providing added support for the substantial stress forces generated
during the crushing operating, the crusher head 53 is mounted in
abutting engagement with a plurality of hydrostatic bearings 125
mounted on thrust seats 127 spaced generally equidistantly around
the crusher axis 47. A bottom surface 129 of the crusher head 53
is spherically shaped, with the center of curvature thereof located
at the apex 63 such that the abutting engagement between the hydrostatic
bearings 125 and the surface 129 form a sliding interface as the
crusher head 53 gyrates and rotates during the crushing operation.
The thrust seats 127 are mounted on and jointly supported by an
upper end 131 of the encasement portion 103. Selected ones of a
plurality of shims 133 having different thicknesses provide the
desired loading of the taper bearings 107 109. In so doing, the
eccentric member 101 is precisely located, both axially and radially,
relative to the encasement portion 103.
By precisely mounting and locating the eccentric member 101 relative
to the encasement portion 103 with the taper bearings 107 109
a gear 135 such as a bevel gear, can be centered about the crusher
axis 47 and attached directly to the eccentric member 101 thereby
eliminating the more complicated, more expensive and higher maintenance
gear arrangements of prior art crushers. A drive train or drive
pinion arrangement 137 meshed with the gear 135 and connected to
a prime mover 139 through a sheave 141 or other suitable means,
provides means for powering the crusher 1.
The crushing operation is effected by the spacing between the crusher
head 53 and the bonnet 31 or, more particularly, the spacing between
the mantel 55 and the bowl liner 35. A releasable clamping arrangement
143 jams the opposing threads 33 34 against each other to prevent
relative rotation of the threads 33 34 except when desired. Preferably,
the clamping arrangement 143 is activated by hydraulically operated,
appropriately spaced cylinders 145.
Wear occurring on the respectively exposed mantel surface 57 and
the bowl liner surface 37 tends to increase the spacing therebetween.
Consequently, the adjusting means 7 which provides the ability
to make periodic corrective adjustments of the spacing between the
mantel 55 and the bowl liner 35 includes the threads 33 34 which
permit continuous adjustment of the axial position of the bonnet
31 in a stepless up or down displacement by rotating the bonnet
31 clockwise or counterclockwise, as appropriate, about the crusher
axis 47 with respect to the upper frame portion 25. Additionally,
the adjusting means 7 may be utilized to adjust the size of crushed
product produced by the crusher 1.
To adjust the separation between the mantel 55 and the bowl liner
35 the hydraulic cylinders 145 are bled whereby the jamming pressure
between the opposing threads 33 34 is reduced allowing the mating
surfaces of the threads 33 34 to be displaced relative to each
other. If it is desired to increase the separation between the bowl
liner 35 and the mantel 55 the threads 33 of the bonnet 31 are
rotated relative to the mating threads 34 of the upper frame portion
25 such that the bonnet 31 is threadably advanced upwardly. Conversely,
if it is desired to decrease the separation between the bowl liner
35 and the mantel 55 the threads 33 of the bonnet 31 are rotated
in the opposite direction relative to the mating threads 34 of the
upper frame portion 25 such that the bonnet 31 is threadably advanced
downwardly. After attaining the desired separation between the bowl
liner 35 and the mantel 55 forces exerted by the clamping arrangement
143 are reasserted to maintain the newly established separation
between the bowl liner 35 and the mantel 55.
Included conical angles of the bowl liner 35 and the mantel 55
are configured to provide an annular space or crushing chamber 149
between the bowl liner surface 37 and the mantel surface 57 the
width thereof generally decreasing downwardly. An annular gap 151
at the lower opening 51 between the bowl liner 35 and the mantel
55 constitutes an annular material discharge opening 153 from the
crushing chamber 149. During operation of the crusher 1 material
is fed into the crushing chamber 149 through the upper opening 49
which material is gravitationally urged downwardly through the annular
crushing chamber 149 and is reduced in size through repeated crushing
contacts between the adjacent surfaces 37 and 57 of the bowl liner
35 and the mantel 55.
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 57 as indicated by
the phantom circle designated by the numeral 155. If desired, a
plurality of flutes 157 may be formed in the bowl liner surface
37 whereby occasional oversized material may be received by the
crushing chamber 149 to thereby increase the maximum opening of
the crushing chamber 149 without increasing the size of the crusher
1.
The lubricating means 9 of the crusher 1 is generally self-contained
and includes an arrangement for circulating lubricant through the
crusher 1 to lubricate the various moving parts thereof. More specifically,
lubricant is pressure pumped from within a casing 159 and/or an
oil pan (not shown) associated therewith, and distributed to each
of the hydrostatic thrust bearings 125 the eccentric mounting arrangement
105 the shaft mounting arrangement 113 the drive pinion arrangement
137 etc.
The pressurized lubricant is conveyed to the interface between
the hydrostatic bearings 125 and the bottom surface 129 of the crusher
head 53 by oil channels 161. The lubricant is sufficiently pressurized
whereby a thin film of lubricant is continuously forced between
each of the hydrostatic bearings 125 and the bottom surface 129
of the crusher head 53. Typically, the thin film of lubricant has
a thickness in the range of approximately 0.005-0.015 inches.
Lubricant sprays outwardly from the interface between the hydrostatic
bearings 125 and the bottom surface 129 and, as it cascades downwardly,
lubricates the other moving parts of the head mounting means 5 therebelow.
Spring loaded wiper rings 163 cause lubricant sprayed radially outwardly
from the hydrostatic bearings 125 to be directed downwardly onto
a seal bearing 165. Lubricant is gravitationally returned to the
casing 159 and/or (unshown) oil pan from the seal bearing 165 and
other pockets by weep holes 167.
The head hold-down means 11 is configured to operably prevent vertical
displacement of the crusher head 53 relative to the eccentric member
101 and the drive pinion arrangement 137 and thereby positively
hold down the crusher head 53 and prevent levitation of the crusher
head 53 from its abutting engagement with the plurality of hydrostatic
bearings 125 during startup, while running empty and awaiting inputting
of additional material to be crushed, etc. In other words, the head
hold down means 11 is configured to apply a downwardly directed
force to the crusher head 53 to supplement the gravitational forces
thereof. For example, such a supplement force of approximately seven
thousand pounds may be sufficient for a fifty-four inch cone crusher.
Of course, the magnitude of such a supplemental force is dependent
on the size of the crusher and the gyrational speed of the crusher.
As the size and/or the speed increases or decreases, the required
supplemental forces accordingly increases or decreases.
The hold-down means 11 includes a plate or retaining cup 169 extending
beneath the shaft mounting arrangement 113 and the main shaft 69
and securing means for securing the retaining cup 169 to the main
shaft 69 such as an elongate bolt or draw rod 170 slidably extending
through a throughbore 171 axially situated in the main shaft 69.
A tapped sleeve 172 has a tapped throughbore 173 configured to threadably
receive the draw rod 170 whereby the draw rod 170 may be "loaded"
by being tightened against Belleville-type washers 174 as shown
in FIG. 1 or loading by other suitable means. The specialized washers
174 permits spacing between the hydrostatic bearings 125 and the
crusher head 53 to slightly relax the minute amount needed by the
lubricant film therebetween.
The sleeve 172 is mounted within a conically shaped fitting 175
configured to prevent axially downward displacement of the sleeve
172 relative to the fitting 175 such as by a snap ring 176 and
rotational movement of the sleeve 172 relative to the fitting 175
such as by a key 177. In addition, the sleeve 172 is mounted by
a thrust bearing 178 in a centrally situated orifice 179 in the
retaining cup 169. As a result, forces generated by the crusher
head 53 which might otherwise cause the crusher head 53 to levitate
from the hydrostatic bearings 125 are transmitted through the inner
race of the spherical bearing 115 to the outer race thereof, preventing
such levitation. The thrust bearing 178 is also configured to permit
rotation of the main shaft 69 relative to the inner race of the
spherical bearing 115 that might otherwise cause the draw rod 170
to threadably detach from the sleeve 172.
A capture mechanism 180 such as one or more detents 181 each
configured to receive a respective spring loaded thruster 182 is
shown in FIG. 3 for example, to prevent the draw rod 170 from rotating
relative to the main shaft 69. A stop mechanism 183 threadably
received in the throughbore 173 and tightened against the sleeve
172 as shown in FIG. 2 provides a reference for readily repositioning
the draw rod 170 relative to the sleeve 172 in order to repeat and
reapply a selected, previously utilized hold-down force of the hold-down
mechanism 11 without measuring to reestablish previous positioning
of the draw rod 170 relative to the sleeve 172.
In other words, a rod head 184 of the draw rod 170 bears downwardly
on a shoulder 185 via the Belleville-type washers 174 preventing
the main shaft 69 from being displaced upwardly relatively to the
retaining cup 169 and the spherical bearing 115. As the spherical
bearing 115 is axially fixedly secured, but not rotationally fixedly
secured, to the eccentric member 101 such as by the counterweight
123 as shown in FIG. 1 by "shrink-fitting", or by other
suitable means, and as the eccentric member 101 and, therefore,
the hydrostatic bearings 125 through the taper bearings 107 109
is axially fixedly secured to the encasement portion 103 the crusher
head 53 and main shaft 69 are prevented from being operably displaced
axially relative to the hydrostatic bearings 125. It should be obvious
that the draw rod 170 rotates and gyrates with the main shaft 69
and the crusher head 53.
Bores 187 and 189 provide access to the rod head 184 for removal,
inspection, or tightening purposes by removal of the mantel bolt
87 such as by a formed depression 190 in the rod head 184 configured
to matingly receive an Allen wrench received through the throughbore
189. If necessary, the mantel cap 95 and the mantel stud 75 may
be removed to provide better access to the rod head 184.
The dust seal means 13 is adapted to isolate inner moving components,
such as the interface between the hydrostatic bearings 125 and the
bearings 107 109 and 115 from abrasive contamination arising from
the ubiquitous dust and grit generated during the crushing process.
The dust seal means 13 includes a flexible seal 191 having an outer
edge 193 secured to a lower extremity 195 of the crusher head 53
and an inner edge 197 secured to an outer race 199 of the seal bearing
165 an inner race 201 of which is secured to the thrust seats 127.
Bearing balls are captured between the inner race 201 and the outer
race 199 in peripheral grooves thereof.
To provide the flexibility needed to compensate for the oscillatory
displacement of the crusher head 53 due to the gyratory motion thereof,
the flexible seal 191 generally has a single-wall construction with
a corrugation-like cross-sectional configuration. As the separation
between the mantel 55 and the bowl liner 35 at a particular point
along the gap 151 approaches the closed side setting, the corrugations
or ribs 205 widen to compensate for the corresponding increasing
separation between the lower extremity 195 and the outer race 199.
Similarly, as the separation between the mantel 55 and the bowl
liner 35 approaches the open side setting, the ribs 205 become narrower
to compensate for the corresponding decreasing separation between
the lower extremity 195 and the outer race 199. To compensate for
rotation of the crusher head 53 relative to the bowl liner 35 during
a crushing operation, the outer race 199 rotates with the crusher
head 53 peripherally relative to the inner race 201.
It is to be understood that the dust seal means 13 may comprise
other arrangements provided that the moving parts of the crusher
1 are isolated from the abrasive byproducts common to crushing operations.
The tramp iron relief system 15 includes means for hydraulically
providing substantial hold-down forces between the upper frame portion
25 and the lower frame portion 21 and for simultaneously providing
the ability to allow the bowl liner 35 to automatically elevate
relative to the mantel 55 whereby non-crushable material can be
rapidly and automatically ejected from the crusher 1 such as a
tramp iron relief system as taught in U.S. Pat. No. 5718390 entitled
"GYRATORY CRUSHER", which is incorporated herein by reference.
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 as appropriate to clamp the upper frame portion
25 to the lower frame portion 21 particularly across the V-seat
arrangement 29.
The closed side setting is adjusted by displacing the bowl liner
35 upwardly or downwardly as needed. Lubricant is pumped to the
hydrostatic thrust bearings 125 the eccentric mounting arrangement
105 the shaft mounting arrangement 113 and the drive pinion arrangement
137. The prime mover 139 is drivingly engaged with the sheave 141
to initiate gyration of the crusher head 53 relative to the bowl
liner 35.
Rock, ores or other materials are dropped through the upper opening
49 of the bowl liner 35 and are crushed between the mantel 55 and
the bowl liner 35 as the material being crushed is gravitationally
urged through the crushing chamber 149 to be discharged through
the gap 151 thereof.
As non-crushable material that is too large to be processed through
the crushing chamber 149 sometimes referred to as "tramp iron",
is dropped into the crushing chamber 149 a portion of the bowl
liner 35 and the associated portion of the upper frame portion 25
are forced upwardly from the crusher head 53 causing the corresponding
portion of the V-seat arrangement 29 to separate, allowing the tramp
iron to pass through the crushing chamber 149 whereupon the upper
frame portion 25 immediately, hydraulically returned to its normal
position relative to the lower frame portion 21.
As the V-seat arrangement 29 is disturbed, such as during passage
of tramp iron or "bowl float", stop pins 207 prevent rotation
of the upper frame portion 25 relative to the lower frame portion
21. Sleeves or inserts 209 as well as the stop pins 207 are readily
replaceable to facilitate replacement of worn parts.
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. |