Abstrict It has been said that the wheel is the greatest invention of all
time; when horses or oxen pulled wagons, dirt roads or no roads
sufficed, but the wheels of modern transportation require paved
roads for cars and trucks, concrete air strips for airplanes, ballast
for railroads, concrete for dams, buildings, and many other things.
Rock is the material that answers all these needs, but rock must
be crushed to usable sizes. Big boulders or quarried rock are crushed
by primary stage jaw or very large gyratory crushers that reduces
the rock to sizes that second stage crushers can accept, and if
the rock needs to be very small a third stage is used. Cone crushers
are the crushers of choice for second and often for third stage
crushing which is the type crusher of this patent application.
Claims Having thus described our invention, we claim:
1. In a crusher of the gyrating cone type: a main frame supporting
an annular base plate, a conical hollow spindle, an eccentric member,
a cone head on said eccentric member, a hydrostatic lubrication
between spindle and eccentric and conehead and hydrostatic lubrication
to a spherical trust bearing; flow dividers proportioning lubricant
to specified ports; hydraulic and threaded means retaining a conical
wear mantle to said conehead; eccentric member attached to a drive
plate with counterweights; double reduction gearing, a spherical
thrust bearing, and an upper frame consisting of a bowl nut having
internal threads lubricated from exterior means, and a threaded
bowl within said bowl nut containing a replaceable conical wear
liner retained by wedging means; an annular band with vertical bars
on its exterior bolted to said bowl, and opposed housings containing
hydraulic means to turn said bowl attached to said bowl nut; multiple
hydraulic cylinders having attaching means at their closed ends
are joined by linking means to anchoring means welded to said main
frame and have their rod ends joined to hook like means that hook
over the flange of said bowl nut with self aligning means; all said
hydraulic cylinders are joined by sealed tubes to accumulator means
that are gas pressurized; said cylinders operate in a pulling mode
to hold said bowl nut firmly on seating means of main frame, and
means to tilt cylinder and hooks outward to rapidly facilitate removable
of upper frame assembly; said flow dividers positioned on exterior
of main frame direct lubricant flow from outside of said main frame
through protective ducting to chambers under said annular base plate
where internal oil lines conduct lubricant and coolant to designated
connections; multiple depending anti-rotation stops restrain bowl
nut to main frame from tangential movement relative to main frame
and act as supports when upper frame is detached from main frame.
2. In a crusher as in claim 1: said main frame having a circular
wall of rolled steel plate, top and bottom flanges, crossbeams full
depth at their midpoint and radially a designed distance then tapering
convergently to maintain approximate uniform strength, and having
end plates welded to said beams, said endplates machined radially
to match the inside diameter of said circular wall, and all parts
joined by secure welds.
3. In a crusher as in claim 1: said main frame having full depth
crossbeams machined radially across their top a designed distance
to fully support an annular plate centered on said beams and securely
welded to said beams; below said annular plate three quadrants formed
by arcuated steel walls of a designed depth having threaded holes
in their lower edges for retaining cover plates, and a first quadrant
for enclosing and supporting gearing means; said annular plate machined
to support and retain an upright conical member, sealing means,
an antifriction bearing, and is drilled and threaded for lubrication
piping.
4. In a crusher as in claim 1: an upright spindle flanged at its
lower face for bolting to an annular plate and having a cylindrical
section extending upward from said flange a designed distance and
containing a hollow cylindrical chamber for partially enclosing
a gear; above said cylindrical section a converging conical section
having a taper large enough to prevent radial clamping by an overlaying
member and above said taper a second cylindrical section; said upright
spindle is cast hollow for weight saving and for circulation of
a heating or cooling liquid; said upright spindle configured to
support and retain a spherical thrust bearing member and a cylindrical
chamber capped at its bottom end, and its top end welded to a machined
opening in said upright spindle.
5. In a crusher as in claim 1: an upright conical member having
multiple oil holes positioned to supply oil pressured to provide
hydrostatic lift and lubrication to lower and upper zones on its
conical surface between said upright member, and an eccentric member
journalled on said upright member; said upright conical member having
a conical taper angle larger than any conical angle that might permit
radial clamping by shrinking of a member rotating on said conical
member.
6. In a crusher as in claim 1: an upright conical member bolted
to a base plate; oil ways drilled to supply oil to each of multiple
vertical grooves or recesses on its exterior taper and to two annular
grooves between a conical lower zone and a conical upper zone and
to a cylindrical extension above said conical upper zone.
7. In a crusher as in claim 1: an upright column drilled and ported
with multiple holes from its bottom face to recessed elongated pockets
machined into its conical surface at designed positions, and other
holes to its top end that engage smooth bore holes parallel to the
axis of said upright column; short cylindrical members having axial
holes and sealing means on their outer surface are inserted in said
smooth bore holes and extend through shims into a thrust bearing
member bolted to the top face of said upright column.
8. In a crusher as in claim 7: a member having a conical inside
taper to match the taper of an upright tapered column journal on
said upright column and has an outer conical taper larger than its
inner conical taper, and the axis of said outer taper intersects
the axis of the inner conical taper at a designed distance above
said member and diverges outward from the axis of said inner conical
taper as it projects downward; the plane formed by said axis passes
directly through the center of gravity of an extension of a counterbalancing
member to which said conical member is attached.
9. In a crusher as in claim 1: a rotatable one piece eccentric
member normally composed of cast bronze or other suitable bearing
material; the bottom face of said eccentric member is drilled and
threaded for cap screws and keywayed for drive keys for attaching
to a driving counterbalancing member; said eccentric member having
a conical bore and a larger conical outer surface and inner and
outer cylindrical extensions concentric to their respective axis;
said cylindrical extensions have arcs subject to radial loads separated
by recessed arcs that are not loaded.
10. In a crusher as in claim 1: a counterbalancing plate member
having a radius through an arc of approximately 180.degree. and
tangential sides extending to an arc of longer radius forming a
counterweight with means to add additional counterweighting means
as required to achieve dynamic balancing of a gyrating mechanism,
and a means to attach a gear and sealing means to its lower face,
and its top face having a means to attach a conical eccentric member
and configured with a recess canted 90.degree. to an eccentric axis
and sealing means.
11. In a crusher as in claim 1: a concentric counterbalancing member
of designed thickness having a perimeter with one radius through
approximately 180.degree., tangential extending sides, a longer
radius from one tangential side to the other tangential side and
having a bored hole concentric to said two radii and to the axis
of the inner conical bore of a rotating eccentric conical member
and has a larger bore than the diameter of the lower cylindrical
section of a nonrotating upright conical member that it surrounds,
and the lower face of said counterbalancing member operates 90.degree.
to its axis of rotation, and a portion of its upper face is recessed
parallel to its lower face where it is attached and keyed to said
rotating eccentric member; an outer recessed portion of said counterbalancing
member is canted 90.degree. to the eccentric centerline of said
eccentric member which has an axis angular to the axis of rotation;
said canted portion is machined to retain a sealing ring and has
annular recess for operating clearance for the rim of a gyrating
eccentrically canted member and for draining lubricating oil and
holes for draining said oil, and its top surface supports adjustable
counterweighting means.
12. In a crusher as in claim 1: a rotating member attached to an
eccentric member and having an arc of extended radius and thickness
to serve as a counterbalance and support for attaching additional
counterweight plates as maybe required and embedded upright pins
and cap screws to hold said additional counterweights against centrifugal
forces and spaces between counterweight plates to allow fine dust
to be ejected and to minimize dust buildup on the inside radii of
said counterweights and spacing washers surrounding said upright
pins and cap screws and having means to attach fine tuning counterweights
to the underside of said rotating member and to do so without being
hindered by any other members of the machine.
13. In a crusher as in claim 1: a gyrating member having an inner
conical bearing surface matching the outer conical surface of an
eccentric rotating member attached to a counter-balancing member
driven by a two stage gear reduction, and said gyrating member has
an outer conical surface upon which is mounted a conical wear resistant
member; said wear resistant member seats tightly on a conical raised
portion starting at its largest diameter and converging for a designed
distance and is integral with said gyrating member, and forms a
spaced apart relatively narrow gap inward for containing a self
hardening liquid and continuing to a smaller conical opening where
it contacts a washer having a conical outer rim and conical inner
opening; a large cap screw having a head with a matching conical
diverging surface seats within said washer; above said conical diverging
surface a converging conical extension of said cap screw; the top
face of said cap screw is configured to be turned with a wrench;
the lower extension of said cap screw is threaded to turn freely
into a female thread of a piston like extension threaded into a
larger diameter piston with tapered threads tightened to refusal
and sealed with an anaerobic sealant thread locker, and said larger
piston has an elastomer sealing ring within an annular groove around
its perimeter; said large cap screw having a partially threaded
hole through on its centerline for retaining a wear resistant cap
and access to hydraulic fittings.
14. In a crusher as in claim 1: a hydraulic operated piston having
a lower diameter larger than the diameter of an upward extension
thereby forming an area to achieve hydraulic force; said larger
diameter having an elastomer sealing ring sliding in a bore near
the top of a conical gyrating member, and said extension sliding
in a smaller bore in the same gyrating member, and an elastomer
sealing means positioned in said gyrating member to surround said
extension, and said extension having an internal female thread extending
downward to a flat face that is drilled and taper threaded to a
designed depth where an angled hole intercepts it; said angled hole
exits at the juncture of said cylinderical extension and said larger
diameter; a valving mechanism engages said taper threaded hole,
and has a commercial hydraulic fitting to receive an oil pump nozzle
followed by a spring loaded check valve, and a second valve seated
by a cap screw and an exit port above said seat; means to access
said valve with an extended oil pump nozzle and an extended wrench.
15. In a crusher as in claim 1: a hydraulic pulling piston embedded
within a gyrating member and having sufficient area to adequately
retain a gyrating wearing member and having at least one pin pressed
into axial parallel holes in its disc, and said at least one pin
projecting into respective clearance holes in said gyrating member
to prevent said piston from rotating relative to its position within
said gyrating member.
16. In a crusher as in claim 1: an upright conical member attached
to a base plate at its largest diameter; a thrust bearing member
attached with a force fit to the top of said upright member and
shimming means for vertical adjustment; cap screws retaining said
thrust bearing member and passing through said shimming means to
prevent shims from moving; said shims insertable and removable with
thrust bearing in place, and a jacking means to provide clearance
between the top of said conical member and thrust bearing's seating
face to provide space for inserting and removing shims and for extracting
said thrust bearing member.
17. In a crusher as in claim 1: a lower part of a thrust bearing
member having an attachment to an upright conical member for support;
a steel member configured to said upright conical member an opposed
face having a concave spherical surface the radius of which is centered
at the vertex of the axis of said upright conical member and the
axis of an eccentric member said radius of a length somewhat longer
than the finished surface of said thrust bearing; an overlay of
bronze or other bearing quality material deposited on said spherical
concave surface and of a sufficient thickness to be machined and
to retain an adequate wear life and to have a finished spherical
surface having the correct radius and said thrust bearing member
having an opening through its axial center to provide operating
clearance for a gyrating universal joint.
18. In a crusher as in claim 1: a metal disk flat on the one side,
the opposed side having a spherical shape with a radius equal to
the distance of said spherical side to the vertex of two converging
axis, and said spherical surface is hardened and super finished;
said disk is centered in a recess directly below a hydraulic pull
piston and is retained by cap screws; said disk having a center
recess to contain a universal joint; with one half attached to the
bottom face of said recess by cap screws, and its other half having
one half of a jaw clutch attached to it; said jaw clutch having
means to self align for blind assembling with its mating half; said
mating half is attached to one half of a slip spline; the other
half of said slip spline is joined to one half of a second universal
joint; a preloaded coil spring surrounds the assembly of joined
splines; a retaining means prevents the spring from disengaging
said spline; a hydraulic motor is suspended by a flanged tubular
means attached by cap screws to a shouldered recess in an upright
column, and said motor is attached by bolts to the lower face of
said tubular member; the lower universal joint is coupled to the
motor shaft; a valving mechanism permits free flow of oil though
the motor and retrograde rotation but stops or resists oil flow
in the direction of an eccentric rotation; a spring loaded adjustable
valve will bypass oil if torque motor exceeds certain pressure,
and the entire mechanism is contained within a fluid tight enclosure.
19. In a crusher as in claim 1: a hydraulic motor is suspended
by a flanged tubular member within a liquid tight chamber; said
tubular member has an outward flange at its top end that is retained
in place by cap screws within a recessed conical member; its bottom
end is flanged inward and bored to match the centering boss of said
hydraulic motor and is drilled and threaded for attaching said motor
by bolts and locking nuts thereby holding the body of said motor
against rotating; a universal joint is coupled to said hydraulic
motor, and valving retards motor shaft rotation in one direction
only.
20. In a crusher as in claim 1: rectangular members drilled and
threaded to conduct lubricant and to conduct heating or coolant
fluid from the exterior of a main base wall to within specific chambers
under said base plate, and their outer ends connected by piping
to flow dividers, and their inner ends connected to individual piping
which connect to specific holes through said base plate, and their
exterior surfaces of said rectangular members are protected from
abrasion by crushed products.
21. In a crusher as in claim 1: lube oil lines from flow dividers
to lube oil passage ways drilled through rectangular members; separate
oil lines conduct controlled volume of lube oil from said rectangular
members to individual connectors in said base plate.
22. In a crusher as in claim 1: an upright conical member attached
to said annular base plate member by cap screws and having larger
conical zone below an annular groove and a second annular groove
above the first annular groove and a smaller conical zone above
said second annular groove and individual means to supply lubricant
to each groove from a two part flow proportionater; holes drilled
through the wall of said eccentric member having their inner openings
approximately centered to said grooves and extending radially to
individual elongated pockets machined into the outer conical surface
of said eccentric member; said first groove connects to pockets
in the lower larger zone, and the second groove connects to pockets
in the smaller upper zone; the outer ends of each hole are taper
threaded to receive nozzles with holes sized to proportion lubricant
volume to each pocket as required.
23. In a crusher as in claim 1: an annular base plate drilled for
multiple lube oil holes spaced apart as designed; the bottom ends
of said oil holes threaded to receive oil fitting connectors; the
top ends of said oil holes recessed concentric to each of said oil
holes to receive oil seals, two larger holes for entry and exit
of a heating/cooling fluid machined and sealed similar to said lube
oil holes; said base plate recessed to receive and hold an upright
conical member against shearing forces, and holes aligned to oil
holes in said conical member, and holes aligned to said heating/cooling
fluid holes in said conical member, and threaded holes aligned to
bolting holes drilled through a flange of said conical member.
24. In a crusher of the gyrating cone type: a main frame containing
or supporting all the gyrating mechanisms, driving means, and support
means to an upper frame assembly; said main frame having an upstanding
male vee ring pressed into the top inside diameter of said main
frame upon which seats a separable upper frame called a bowl nut
having a matching inverted annular female vee groove that is formed
integral within said upper frame, an annular flanged diameter section
rising above said vee groove and extending to a larger diameter
than said vee groove; extending outward of said larger diameter
are platforms for attaching adjusting mechanisms and antirotation
stops; inward from said vee groove is an annular vertical extension
having an opening containing a section of female threads which extend
upward above said annular flange to a smaller diameter flange positioned
a designed distance above said vee groove; below said threads an
annular cavity slightly larger in diameter than the root diameter
of said female threads; below said cavity an annular surface slightly
smaller in diameter than the inside diameter of said female threads
and projecting downward below the lowest edge of said vee groove
with an annular groove machined in its inner surface; the outer
diameter of the upward projecting section has multiple angled braces
evenly spaced circumferentially and having openings within said
braces for retaining hydraulic hoses; above said smaller diameter
flange is a separate annular ring having the same outside diameter
and one or more threads having the same inside diameter, pitch,
and contour as said female thread; said threaded ring is restrained
against rotation by pins but is movable vertically a limited distance;
said pins having enlarged diameter heads and shouldered within said
ring and stepped holes shouldered in the top flange of said upper
frame and are retained by threaded means; multiple hydraulic cylinders
having rectangular bodies are bolted to the under face of said top
flange, and all cylinders are connected in series by metal tubing
or hydraulic hoses and have one or more connections to hydraulic
oil supply; centered above piston in each cylinder are holes through
said top flange, and in each hole are push rods of a length equal
to the distance from the top face of said top flange to the pistons'
lowest positions in said cylinders; a rotatable annular member having
a cylinderical outer diameter extending from its lowest edge a designed
distance to male threads, having a matching pitch and contour to
said female threads, extends to the top surface of said annular
member where bolts attach an annular plate having an inside diameter
centering on said rotatable member and an outside diameter slightly
larger than the outside diameter of the top flange of said upper
frame; a cylindrical band of designed width has its top edge welded
to the rim of said annular plate, and around said band are welded
equally spaced steel bars parallel to the axis of said rotatable
member; mounted on two extended platforms of said upper frame 180.degree.
apart are upstanding chambers having inner walls concentric to said
rotatable member and spaced apart outer flat walls; contained within
each chamber is a slidable rectangular means guided by rollers near
each end of chambers; said rollers turn on interlocking axles with
one axle removable before other axles can be removed and is inserted
after three axles are inserted; an arm welded to one axle is retained
by a cap screw and all axles are restrained from turning; hydraulic
actuated pawls pivot on rectangular means engaging and disengaging
steel bars simultaneously, and pivoting hydraulic rams push/pull
rectangular means the chordal distance between bars, means to supply
all hydraulic means with hydraulic power; means to restrain upper
frame from lifting while crushing crushable material but yields
to noncrushable objects and means to restrain said upper frame from
creeping circumferentially, said rotatable member having a conical
inner concentric surface larger at its lowest edge and converging
upward to a central opening; a seating surface for a replacible
conical means having a top outward flange slightly smaller in diameter
than the central opening of said rotatable member with a conical
under surface; sliding wedges engage said under surface and are
urged inward by thrusting means and are clamped vertically and enclosure
means to protect against entry of rain and solid matter.
25. In a crusher as in claim 24: an annular frame having an inverted
vee shape, a concentric female thread; two opposed extended platforms
supporting attached upstanding means to power turn a rotatable threaded
member, and multiple extending platforms for attaching downward
projecting beams; said beams bear against reversible stop blocks
attached to platforms welded to the underside of the top flange
of said main frame.
26. In a crusher as in claim 24: a means of adjusting the space
between a fixed wear member and a gyrating wear member to control
product sizes and compensate for wear and to separate a rotatable
member from a fixed member, said means of adjusting to be a fixed
member having a female thread and a rotatable member having a male
thread, said threads to be angled on their loaded faces at larger
angle than the bisecting angle of the crushing chamber to avoid
outward radial sliding; the female thread to have a greasing groove
its full length with both ends blocked and blocked intermittently;
lubrication holes from said groove between each blockage to the
exterior of said fixed member; manual or automatic means of injecting
grease into said holes.
27. In a crusher as in claim 24: a means to clamp a rotatable member
from turning within an upper frame member while the machine is crushing;
said clamping means to be a ring like member having at least one
full internal thread and a means to restrain it from rotating, said
clamping means to be forced vertically by hydraulic means, said
hydraulic means to be multiple rectangular members bolted to the
underside of a top flange of said fixed member, said rectangular
members bored for short stroke pistons and connected in series by
hydraulic lines and to a pressure source at one or more spaced places;
centered over each piston is a vertical hole through said flange
with a push rod reaching from a fully relaxed piston to flush with
the top of said flange, and with all moving parts totally enclosed
to prevent entry of moisture, dust, or other contaminants.
28. In a crusher as in claim 24: a power means to rotate a rotatable
member positioned within a threaded bowl nut said power means having
two enclosed housing each having an arcuated inner wall centered
off the main axis of said bowl nut; an outer wall tangent to said
arcuated inner wall and spaced outward by members at ends of said
walls; said inner wall and lowest end spacers welded to a base plate
that is drilled for bolting attachment; within each said enclosed
housing is a slidable member that extends through openings in uppermost
end spacing members, roller assemblies near each opening guide said
slidable member, a push-pull hydraulic means is pin connected to
said slidable member and to a spacing member; said slidable member
is angled to a thread angle; a swingable pawl journalled to the
inside face of said sliding member has its pivoting axis parallel
to the centerline axis of said rotatable member and having vertical
bars at end of pawl and parallel to the same axis; said bars spaced
to closely straddle multiple evenly spaced vertical lug bars on
a second rotatable member; said pawls are actuated by hydraulic
means; an opening in said arcuated wall to allow said pawl to swing
through and travel within said opening the length of travel of said
sliding member; said sliding member extends beyond said enclosure
at each end of its length of travel with covers to protect said
extensions; a cover member encloses the top of said housing; each
power means bolted to platform extensions integral to a flange of
said bowl nut and 180.degree. apart.
29. In a crusher as in claim 24: a rotatable member having an inverted
conical interior with a designed size of top opening and having
flat surface at top of said opening formed by segmented steel plates
welded over cast cored pockets that form radial struts from an outer
wall to an inner conical wall; three or more evenly spaced slidable
wedges having conical ramps that match the conical flange of a wearing
member and having elongated slots midway of their lengths and vertical
slots at the opposite end of wedging ramps; thrusting means with
bolt heads locked against turning in said vertical slots, nuts on
said bolts, washers, and steel thrust blocks drilled for bolt clearance
and welded to said segmented plates directly above three or more
radial struts; holes drilled and threaded through said plates and
into said radial struts for cap screws positioned to allow wedges
to travel from edge of said opening inward; guides prevent wedges
from skewing.
30. In a crusher as in claim 24: slidable wedging means actuated
by thrusting and clamping means for retaining and releasing a conical
member seated within a rotatable member.
31. In a crusher as in claim 24: two hydraulic powered members
bolted to platforms integral to a non rotating threaded member and
spaced 180.degree. apart for balanced tangential forces; said powered
members having pawls that grip lug bars integral to a rotatable
member for either push or pull directions; said rotatable member
is attached to a second rotatable member that is threaded into said
non rotating threaded member; said pawls are powered to engage and
disengage gripping said lug bars; accumulator means to accommodate
varying hydraulic oil volume pressurized by oil captured between
the pawls' hydraulic cylinders and a control valve as pawls are
forced radially throughout their arc of travel thereby changing
the oil volume within their actuating cylinders.
32. In a crusher as in claim 24: a means to accommodate passing
uncrushable objects through a crusher and to have a means of rapid
disassembling and reassembling of a crusher's upper frame and gyrating
parts by hook like means coupled to tilting hydraulic cylinders
which are connected to anchor means by linkage means; vertical tubing
means slidable in header means with sealing means join cylinders
to horizontal tubing means pivotable and sealed within header means
bolted to anchor means having holes to pass fluid means to accumulator
means.
33. In a crusher as in claim 24: multiple hook like members joined
to concave annular plates seated on convex annular plates positioned
over holes in a flange of a crusher's upper frame; said convex annular
plates have pinning means to said holes; greasing means to inject
grease between convex and concave surfaces; said hook like members
shaped and coupled by pins to devises to allow limited tilting relative
to said clevises, and said devises having female tapered threads
coupled to a matching threads on hydraulic rams to form tight fits
to resist uncoupling; hydraulic cylinders contain said rams and
function in a pulling mode; annular headers threaded into female
threads in said cylinders and seat against tapers with sealing means
and have bushings and seals encasing said rams; extension plates
welded to the bottom covers of said cylinders are offset toward
vertical tubes in proportion to the area of each cylinder less the
area of the ram to the area of the vertical tube's outside diameter
to counter the thrusting force trying to eject said tube; said extension
plates have holes for connecting links and pins for coupling to
anchor means.
34. In a crusher as in claim 24: header plate means aligned on
each side of anchor plate means and retained by bolts through both
header plates and anchor plate and sealed on their contact faces,
and anchor plates having holes of about the same size as hole size
of horizontal tubes; said header plate means having holes bored
at an angle to align with header plates sharing the same horizontal
tubes; said header having sealing means enclosing said horizontal
tubes allowing said tubes to turn in said headers; annular means
shaped to the diameter of said horizontal tubes on one end and their
other end step bored to the diameter of vertical tubes and inside
diameter of said tubes and sealing means enclosing said vertical
tubes and welded over holes in said horizontal tubes inline with
headers fused to cylinders.
35. In a crusher as in claim 24: pivotable tubes journalled in
sealing headers joining multiple cylinder assemblies spaced around
a crusher frame and connected to one or more accumulators; vertical
tubes join headers fused near tops of cylinders to headers fused
to said horizontal tubes; cylinders tilt outward with hook like
means coupled to cylinders or hook like means can be tilted with
cylinders remaining in fixed positions; valving means connect hydraulic
oil supply hose to an anchor plate drilled and threaded to connect
to its manifold oil hole and retain a valve; all said headers have
close clearance fits to tubing means between sealing means and their
outer ends but are tapered bored between said sealing means and
an inner face to accommodate for any misalignment of headers; said
vertical tubes' headers are tapered bored to accomodated angle changes
when cylinders are tilted, and vertical tubes are of a length to
stop tilting after hook like means clear the flange of the upper
frame.
36. In a crusher as in claim 24: a safety relief system for cone
type crushers having one option for tilting cylinders and attached
hook like links as one, and an option of tilting hook like links
only where cylinders with manifolds are not made to tilt.
37. In a gyrating crusher of the cone type: a main frame having
a circular wall and having top and bottom flanges with 90.degree.
cross beams contoured for approximately uniform strength across
their lengths and with end capping plates to distribute weld concentration
where joining to said circular wall; one of said beams full length
and other beams in two sections abutting said one beam and fully
welded to same and said beams full depth at their mid section; a
circular member is centered on said beams and welded to same; said
circular member of ample thickness to support all gyrating members
and non gyrating companion members and having an annular oil drain
recess with multiple drain holes; multiple oil passages and two
heating/cooling fluid passages drilled through said circular member;
three arcuated walls welded to said beams and said circular member
form chambers in three quadrants and in one separate quadrant a
gear chamber; openings in said beams and within said chambers for
oil drains; means to conduct lube oil and heating/coolant fluid
from an outer wall to within chambers formed by said arcuated walls;
formed hydraulic lines from conducting means to specific connecting
means in said circular support member and formed means to conduct
and return heating/coolant fluid without mixing with lube oil and
cover plates to close said chambers; a conical spindle secured tightly
in a recess in said support by cap screws; said spindle having multiple
passage ways for lube oil to specific outlets and with sealing means
between said conical spindle member and said circular support member;
said conical spindle having a hollow internal chamber with a low
entry port with swirling means for circulating heating/coolant fluid
and a high exit tube to insure a full chamber, a sealing means for
said chamber and a sealing means between said spindle member and
said support member, flow dividers and tubing members to distribute
incoming lube oil to specific connectors in conducting members from
outside of said frame wall to inside of said chambers, connections
for hoses to connecting members for circulating heating/coolant
fluid; a horizontal input shaft journalled in roller bearings within
a tubular housing having sealing means, and said shaft having a
spiral bevel gear at its inner end driving a mating spiral bevel
gear of larger size driving its vertical shaft also journalled in
anti-friction bearings and having a spur gear at the top end of
said vertical shaft, means for adjusting the proper meshing of said
bevel gears; said spur gear meshes with an internal tooth gear attached
to a rotatable member which is attached to a conical eccentric member
which rotates on said conical spindle; sealing means between said
rotatable member and said support member; upon said spindle is attached
a spherical thrust bearing vertically adjustable and having sealed
tubular connectors to transfer lube oil between said spindle and
said thrust bearing, hydrostatic means to lubricate said conical
eccentric member and said thrust bearing; oil holes from the inside
conical bore of said eccentric member aligned to annular grooves
in said spindle conduct lube oil into grooves machined into the
outer conical surface of said eccentric member; said holes having
varying sizes of nozzles to meter hydrostatic oil flow to a gyrating
conical member, and resting upon said thrust bearing and journalled
on said conical eccentric member is said gyrating conical member
having a replacable wearing member retained on said gyrating member
by hydraulic and threaded means; said gyrating conical member is
restrained from turning in one direction but is free to turn in
the opposite direction; hydraulic motor, valving means, universal
joints with slip shaft and a jaw clutch are restraining means; sealing
means between said gyrating conical member and said rotatable member;
said main frame has a vee-ring inserted into its top flange and
upon said vee-ring rests a flanged member having an internal thread
that has a groove in its loaded face; said groove is blocked at
both ends and has intermittent blocking between said end blocking;
between said intermittent blocking are lubrication means into said
groove; at the bottom flange of said main frame multiple spaced
apart anchor members are attached; all but two of said anchor members
are ported for fluid passage, bolt holes above and below said ports;
header means each side of said anchor members, said header means
bored and sealed to align to headers on adjacent anchor members
and sealed between header means and anchor members; hydraulic tubular
manifolds extend from within header to within the next header except
at power input sector and having one or more slip connectors, with
sealing means, 90.degree. to said manifolds said manifolds turnable
within said headers; said anchor members drilled and pinned and
linked to hydraulic cylinder means; vertical tubular members join
said manifolds to said cylinder means; a rod means projecting from
within said cylinder means is threaded into a clevis means; an extended
hook like means is pinned to said clevis means and projects inward
over said flange of said threaded member and is seated on said vee-ring
with self aligning means between said flange and said hook like
means; accumulator means connected in series with said manifolds
and said accumulators are gas pressurized to a specified pressure
range; hydraulic fluid is pumped into said manifolds, cylinders
and accumulators to a specified volume and pressure; said cylinder
means and said hook like means can be tilted outward after pressurized
hydraulic fluid is drained to a reservoir; gas pressure in accumulators
is retained; said threaded flanged member contains a rotatable threaded
member that is free to be turned by powered means when unlocked;
locking means is a ring with one or more threads above said flanged
threaded member and is prevented from turning but can be moved vertically
by multiple hydraulic rams bolted to the under face of the top flange
of said flanged member; means thereby locking and unlocking said
rotatable member; said rotatable member contains a replaceable wearing
member that is retained in said rotatable member by sliding wedges
having slotted means for clamping by cap screws after being forced
inward by thrusting means; means to prevent circular movement of
said flanged threaded member relative to main frame member by downward
projecting means attached to said flanged member bearing against
blocking means attached to the top flange of said main frame.
Description BACKGROUND OF THE INVENTION
Nations can only have an advanced structure and mobile society
if they have paved roads, railroads, airports, dams, buildings,
foundations for houses, and countless other things that require
crushed rock and other rock products; in fact, all people live in
an ongoing Stone Age and always will. The volumes and tonnages of
sand, gravel, crushed rock, cement, and ore far exceeds any other
products in the United States. As in most businesses there is substantial
competition both within the producers of rock products, and also
those who manufacture machinery for such purposes. Gyrating cone
crushers are the machines of choice for crushing the harder and
more abrasive rock. The more efficient, durable, and economical
a cone crusher can be the better it serves all concerned. Rock crushers
should be structurally very strong to withstand the enormous pressures
imposed, yet should not be so over designed that they become too
heavy and too costly. It is more logical to use portable crushing
plants at nearby rock sources to the places of use than if the hauling
distances are too far from stationary commercial rock sources to
the places of use; plus portable crushing plants can be built for
much greater production, e.g. for highway construction, than most
commercial plants. Crushers for portability must be of compact dimensions
and low weight consistent with acceptable capacity and low maintenance;
such a machine is the subject of our request for patent rights;
it has several new concepts that will prove to be extremely advantageous
for both portable and stationary use.
SUMMARY OF THE INVENTION
According to the present invention and forming a primary objective
thereof, a novel combination of means to construct a very rugged
and efficient rock crusher of the gyrating cone type, and to achieve
this objective by designing a machine that is of less weight, lower
costs to manufacture, easier to service, and more user friendly
than other makes of this type of rock crushers now known. The first
means is a new concept of main frame that eliminates a massive annular
gear chamber and a hollow center for bearings or an embedded post
shaft either of which is used by all other makes of gyrating cone
type crushers. Our new design provides simple full depth straight
crossbeams to better resist the enormous forces of crushing rock,
ore, or other materials by the compression method of crushing. The
second means is to have a better bearing concept that is far less
costly than roller bearings but will run as accurately, and a bearing
that is not subject to thermal clamping seizures as are bushing
type bearings. A third means is the use of a double gear reduction
drive between power input and an eccentric that gyrates the crushing
member so as to enable the use of higher speed motors which are
less costly than slower speed motors and weigh less, also smaller
less costly sheaves are used. A forth means is a new concept to
restrain the gyrating member from spinning when the crusher is running
but not being supplied with crushable material. A fifth means is
a novel way to hold a cone head mantle firmly in place by hydraulic
clamping and release. A sixth means is an improved method of retaining
a bowl liner within a bowl member with slidable wedges. A seventh
means is a totally new concept of a tramp metal relief system where
hook like means can swing outward to enable rapid removal of a bowl
assembly. An eighth means having an adjusting system contained in
a rigid enclosure that protects the entry of stray rocks or similar
and rainfall. Within said enclosure a slidable member guided by
roller means and actuated by hydraulic means and having a pivoting
pawl to engage vertical spaced apart lugs attached to a ring like
member; said hydraulic means push and pull said slidable member
that will turn said ring like member when said pawls are engaging
said lugs. Said pawl engages and disengages said lugs by hydraulic
means. Two of said enclosures are used and are 180.degree. apart
for balanced thrust.
BRIEF DESCRIPTION OF THE DRAWINGS
Having introduced the purpose of this application, we now list
the numbers that we have assigned to its parts. We refer to FIGS.
1 through 49. The purpose each part serves will be explained later.
FIG. 1 is a perspective view of our fully assembled rock crusher;
1-MF is the main frame; 1-BA is the bowl assembly; 326 is an adjusting
unit; 341 is a gas charge accumulator; 281 are hook-like members;
275 are hydraulic cylinder assemblies; 294 are anchor plates; 293
are manifold tubes; 290 are manifold to cylinder tubes; 298 are
thrust absorbing members; 24 is a lube oil drain; 224 are anti-rotation
stop blocks; 222 are depending arm anti-rotation stops; 220 is a
bowl nut; 243 is an adjustment ring.
FIG. 2 shows a perspective view of the main frame with hydraulic
cylinders 275 and hook-like members 281 tilted outward; 276 are
connecting links; 1-BF is a base flange, and 1-W is a cylindrical
wall of the main frame 1-MF; 218 is a V-ring; 119 is a wear mantle;
342 are lifting brackets.
FIG. 3 is a vertical section view through the crusher; 331 is a
spacer brace and a wear protector; 263 is a wear liner; 333 is a
large socket head cap screw; other numbers are detailed in subsequent
FIGs; plus other numbered features that cannot be shown in this
view.
FIG. 4 is a plan view of the lower half of the main frame; 1-BF
is the bottom flange of said main frame; 2 are beams; 3 are end
plates welded to beams; 4 is a bearing housing support with precision
bore 22 and drain port 24 integral; 5 are support plates for 4;
7 is a bearing housing support; 23 is a precision bore in 7; 6 are
arcuated walls; 9 are upright members; 10 is a circular plate member;
12 is a centering pin in 10; 12-H is a centering hole in beams 2;
11 are lube oil conducting members; 8 are attachment shelves; 20
are cover plates;
FIG. 5 is a vertical sectioned view through B B' FIG. 4; 35 are
oil drain ports in beams.
FIG. 6 is a vertical sectioned view taken through C C' of member
10
FIG. 7 showing centering pin 12 17 are lube oil holes, 19 are
threaded holes, 18 are drain holes, 13 is an oil deflector ring,
28 is a precision recess, 29 is seal groove, 32 is a seal ring shoulder.
FIG. 7 is a plan view of member 10: 21 is a precision bore, 30 is
a gear inspection hole, 142 is a lube hole 14 is an oil trap; 33
and 34 are larger oil holes than 17 25 and 26 are heating/cooling
fluid holes, 27 is an annular oil drain;
FIG. 8 is a detail view through E E': 16 are recesses for elastomer
seals at the top ends of all oil and heating/coolant holes shown
in FIG. 7.
FIG. 9 is a detailed view of 13 and 27 taken through F F' FIG.
7;
FIG. 10 is a detailed view taken through D D' of FIG. 7 showing
deflector 14 and nozzle 15.
FIG. 11 is a plan view of the top of member 38 a fixed spindle;
40 is a bolting flange with counterbored holes 41; 42 are flutes
(grooves) with tapered edges; 44 are three evenly spaced smooth
bored holes; 45 are evenly spaced threaded holes; 47 is opening
for a gear; 46 are multiple threaded holes in a recessed face; 43
is a conical surface;
FIG. 12 is a vertical view of 38; is a large diameter of taper
43 and ' is its small diameter; 48 is a cylindrical extension of
' diameter; 49 are hydrostatic lubrication grooves; 39; are annular
grooved lube oil distributors.
FIG. 13 is a detail of grooves 39 and 55 oil lines;
FIG. 14 details transfer nipples 50 with one of two elastomer seal
rings 51 in place.
FIG. 15 is a plan view of the bottom face of spindle 38; 41 are
multiple bolt holes; 52 are multiple lube oil holes; 55 are oil
holes; 53 is a fluid inlet; 54 is a fluid outlet;
FIG. 16 is a vertical sectioned view of spindle 38 taken through
gear opening 47; 61 is a cast hollow chamber; 62 is an overflow
exit tube; 57 is a fluid tight tubular chamber; 56 is a precision
bored recess; 58 is a solid disk; 59 is an elastomer seal ring in
58; 60 is a retaining ring;
FIG. 17 is an enlarged view of annular grooves 39
FIG. 18 is a vertical view of 65 a conical eccentric member; 66
are flutes with tapered edges; 68 are oil holes with tapered threads
at outer ends; 70 is a keyway; 2X is the diameter between A-1 and
A-2 arcs, FIG. 19.
FIG. 19 is a plan view; 67 are slots open at the large end of the
taper of 65; A-1 is an arc of less than 180.degree.; A-2 is a smaller
arc than A-1; X are radii between said arcs and of shorter radius
than said arcs.
FIG. 20 is an enlarged view of 68;
FIG. 21 is an enlarged view of nozzles 69.
FIG. 22 is a vertical sectioned view through the plane of the eccentric
65; 64 is a cylindrical extension concentric to centerline 102;
63 is a cylindrical extension concentric to centerline 101; 72 is
an annular groove; 72-H are oil vent holes; 69 are nozzles; 74 is
a centering bore; 101 is the centerline of inner cone 73; 102 is
centerline of outer cone of 65; angle .alpha. is established by
101 and 102;
FIG. 23 is a plan view of the bottom; 70 are one or more keyway
slots; 71 are multiple threaded holes on radius R-5.
FIG. 24 is a plan view of the eccentric drive plate 150; is the
eccentric offset and the center of radial line R-1; radii R-2 R-3
and R-4 are centered on the machine's center line 101; /2 is the
center of R-5 bolt circle; 192 are cap screw holes on said bolt
circle; 70 are keyways; 18 are multiple lube oil drains; 155 are
up standing bars; 399 are counterweight clamps; 104 are threaded
holes;
FIG. 25 is a vertical partially sectioned view showing eccentric
65 with drive keys 77 an internal tooth gear 130 bolted to 150
155s embedded in 150 and retained by cap screws, and a section of
a labyrinth seal ring 36. 80 are dust seal retaining bosses.
FIG. 26 is a plan view of a section of cone head 75;
FIG. 27 is a vertical view of the exterior cone-head 75; 76 is
a conical area raised above the conical surface of 75; 80 is a dust
seal retaining boss; 119 is a sectioned view of a mantle (wear liner);
FIG. 28 is a plan view of the lower surfaces of 75; 78 are multiple
struts; 79 are cavities; 83 is a flat surface; 85 is a conical surface;
86 are precision spaced holes; 87 is a precision bore.
FIG. 29 is a vertical section view of cone head 75; 100 is the
apex of center lines 101 and 102; 103 is the amplitude of gyration;
81 is a converging conical bearing surface; 82 is a cylindrical
bearing surface; 89 is gyrating clearance; 83 is a precision recess
with threaded holes 84 in its face; 92 is a conical surface; 88
is a smooth precision cylindrical bore; 85 is a conical surface;
86 are precision spaced blind holes; 90 is an annular seal ring
groove; 91 is an extended cylindrical section.
FIG. 30 is enlarged vertical section view of an assembled cone
head; 93 is a piston; 94 is a cylindrical extension threaded into
93; 95 is an elastomer seal ring; 96 is an elastomer seal ring;
97 are pins; 105 is a copper ring; 120 is backing material; 98 is
a conical washer-spacer; 99 is a cap screw with a double conical
head; 122 is a protection wear cap retained by cap screw 333 see
FIG. 3; 334 is a set screw and nut; 110 is the body of a valve;
118 is an oil hole; 121 is an oil pump extension; 106 is a spherical
thrust bearing member; 107 are cap screws; 108 is a universal joint;
109 is half of a jaw clutch with a conical extension; 103 is the
amplitude of gyration.
FIG. 31 is an enlarge sectional view of 110; 111 is a ball; 112
is a spring; 113 is a headless screw with a hex hole through it;
114 is a ball; 115 is a vent; 116 is a cap screw; 117 is an oil
gun fitting.
FIG. 32 is a vertical section view through the drive train gearing;
124 is a bearing housing extension of shaft enclosure 156; 125 is
an input shaft journaled in bearings 131; 134 is a bearing adjustment
mechanism; 138 is a sealing member; 139 is a wear sleeve; 329 is
a closure cover; 136 are shims at two places; 137 is a seal ring;
145 is a dike; 126 is a spiral bevel pinion gear; 127 is a mating
spiral bevel gear (both too difficult to draw the teeth); 128 is
a vertical gear shaft; 129 is a spur gear; 130 is an internal tooth
gear; 192 are gear and eccentric retaining cap screws; 133 is a
roller bearing; 140 is a spacer; 141 is a spacer oil slinger; 132
is a ball bearing; 134 is a retaining nut and locking washer; 135
is a bearing housing; 143 is a bearing retainer plate; 142 is an
oil passage way; 24 are oil drains to a reservoir not shown; 36
are dust seals; 37 is a seal ring spacer; 151 are counterweights;
153 are spaces between counterweights; 154 are spacers; 152 are
fine tuning balancing weights.
FIG. 33 is a vertical section view of thrust bearing member 160
mounted on spindle 38; 161 is a bearing quality metal bonded to
160; 163 are adjustment shims; 162 are retaining cap screws; 164
are arcuated closed end galleries machined into 161; 165 are jacking
screws; 50 are lube oil transfer nipples; 174 is the female half
of jaw clutch 109; 158 is a tubular motor mount; 159 are cap screws;
167 is a hydraulic motor; 168 is a valving member; 379 are cap screws;
170 is a universal joint; 171 is a male spline shaft; 172 is a female
spline; 173 is a coil spring; 191 is a port opening in 158; 190
is a vent opening in 158; 166 is a pressure relief vent in 160.
FIG. 34 is a cut away view of 168; 180 is a valve seat; 181 is
a ball; 179 are bolt holes; 182 is stop pin; 183 is a closure of
a machining access; 184 is an oil passage way; 185 is a hole; 186
is a ball; 187 is a coil spring; 188 is a pressure adjusting screw;
189 is a two way oil flow passage; 194 is an optional venting port.
FIG. 35 is a plan view of our hydrostatic lubrication system and
heating/cooling fluid connections; 200 and 201 are flow dividers;
203 is a flow proportionator; 195 196 and 197 are connectors to
hydraulic hoses from a pump source; 198 are fittings; 199 are lube
oil tubes from 198 to flow dividers; 204 and 205 are multiple lube
oil tubes to members 11; 210 are distribution tubes to specific
connections; 207 and 206 are larger tubes with different flow volumes;
208 and 209 are heating/cooling fluid connectors; 292 293 and
295 are detailed on FIG. 42.
FIG. 36 is a vertical section view of the top frame assembly 1-BA;
220 is a bowl nut; 240 is a bowl; 221 are platform extensions of
220; 218 is an annular -ring pressed into the main frame 1-MF; 219
is one of several grease fittings; 222 is a depending arm; 223 is
a platform welded to main frame; 224 is a stop block; 225 is a drain
hole; 263 is a wear liner; 120 is backing; 246 are cavities between
struts 245; 260 are cover plates welded over said cavities; 241
is modified thread form; 242 and 243 form an adjustment ring; 244
are equally spaced lugs welded to 243; 235 is a locking nut; 234
are thrust rods; 232 are pistons; 230 are cylinders; 231 are cylinder
retaining cap screws; 233 are hydraulic lines joining cylinders
230; 245 are gussets forming openings 264; 268 is a depending band
joined to 235; 247 are elastomer dust and moisture seals; 248 is
a hopper for 250; 265 is a bowl wear liner;
FIG. 37 is an enlarge section of female thread 226; 227 is a small
annular groove cut in the thrust flank of 226; 228 are multiple
lubrication holes into 227 and having threads for fittings.
FIG. 38 is an enlarged plan view taken through G G'; 250 is a slidable
wedge; 253 is a thrust absorbing member; 251 is a cover washer;
254 is a bolt; 255 is a nut; 256 is a washer; 252 is a clamping
cap screw; 259 is an elongated slot; 257 is a vertical slot in 250;
258 are guides; 266 is a wedging ramp with a conical radius; 261
is a 360.degree. dike.
FIG. 39 is an enlarged vertical view of part of the top frame 1-BA;
235 a locking nut; 268 is a metal band; 236 is an elastomer seal;
230 is a partially sectioned hydraulic cylinder; 231 are cap screws;
232 are pistons; 245 are gussets; 233 are connecting tubes or hoses;
269 is an expansion/contraction configuration for tubes; 270 is
a hydraulic hose from a power source.
FIG. 40 is an enlarged plan and vertical section view of multiple
cylinders 230; 237 is an elastomer seal; 271 is an oil passage through
230 with a side hole into each cylinder chamber.
FIG. 41 is a tangential vertical view of one assembly of our relief
system; 294 are anchor members; 246 is a hole for oil passage; 299
is a valve; 295 are header plates; 299 is a valve; 276 are links;
277 are pins; 278 are retaining rings; .theta. is a limiting angle;
279 are air filters; 275 is a sectioned view of a cylinder assembly;
is cylinder diameter; is ram diameter; 280 are clevises; .beta.
is a limiting angle; 281 are hook like members; 282 are concave
discs; 283 are convex pads having positioning stems; 284 are precision
holes; 285 are spherical headed shoulder pins; 286 are threaded
blocks with headless screws; is a long radius centered at lowest
277 pin; is a shorter radius centered at clevis pin.
FIG. 42 is a radial view of FIG. 41; 287 is a lubrication fitting;
293 is a tube manifold with slip connector 292 joined to it; 275
is a partially sectioned view of a whole cylinder; 297 are saddle
blocks; 298 shows the top end of a thrust transfer member; 296 is
a threaded hole into one 294; 289 is a 90 deg. attachment to 275;
290 is a connecting tube of diameter; 300 is an air bleed valve;
301 is a spacing pad.
FIG. 43 is a sectioned view of a relief cylinder; 306 is a partially
sectioned piston; 313 is a back-up ring; 314 is an elastomer seal;
315 is a non metallic band; 316 is a pipe plug; 307 is a piston
rod of diameter; is cylinder diameter; ' is a diameter larger than
; 318 is a travel space; 317 are elastomer seals; 323 is a taper
in 292 and 289; is the distance from the center line of 275 to the
center line of 290; is an offset; 303 is a taper; 324 is an eye
plate welded to 275;
FIG. 44: 305 is a threaded cylinder head; 322 is a seal ring groove
308 is an elastomer seal; 310 is a bushing; 309 is a retaining ring;
311 is an elastomer seal; 312 is a rod wiper; 320 are wrenching
flats; 321 is a taper thread; 319 are recesses for pin wrench.
FIG. 45 is a tangental vertical partially sectioned view through
our power adjustment system 326 and part of top frame 1-BA. 222
is a depending arm; 223 is a fixed platform; 224 is a reversible
stop block; 352 is a base plate; 353 are spacing end plates; 354
is a spacer plate with hydraulic couplings through it; 355 is a
spacer plate with slot 356 through it; 357 is an angle iron spacer
and thrust absorbing member; 358 are gussets welded to 357; 382
is a spacer end plate. 350 is an arcuated inner wall; 351 is a flat
outer wall; 360 is a push/pull hydraulic ram; 359 are coupling pins;
361 362376 and 377 are hydraulic hoses; 364 is a sliding bar;
363 is a bracket welded to 364; 365 are guide rollers; 385 are key
axles; 368 are axle locking arms; 383 is a section cut out of wall
350.
FIG. 46 is a plan view of FIG. 45; 242 and 244 are a section of
the adjustment ring 243; 370 is a bidirectional pawl; 371 is its
pivot axle; 372 is an axle locking arm; 373 and 374 are extended
grippers; 375 is push/pull hydraulic ram; and attached to cover
381; 380 are cover guards over 364;
FIG. 47 is an inside vertical section view of one of the roller
assemblies of 326; 367 are axle supports; 385 and 387 are horizontal
axles and 386 are vertical axles; 389 are threaded holes; cap screw
392 locks arm 368.
FIG. 48 is a plan view of FIG. 47; end spacer plate 382 is cut
out for bar 364 at both ends; plates 390 FIG. 47 fill openings above
382.
FIG. 49 is an end view of 326 adjusting assembly; 390s are attached
to cover 381; 391 are clamps to hold 380.
18 is for all drains not otherwise numbered and is used in several
different FIGs.
DETAILED DESCRIPTION OF DESIGN OF PREFERRED EMBODIMENTS
FIG. 1 shows a perspective view of a fully assembled rock crusher
that is the subject of our invention. The numbered parts are shown
in detail on pages 3 through 22 and FIGS. 3 through 49 of the drawings.
In FIG. 1: 341 is one of two gas-pressurized accumulators; a second
accumulator, out of view, works in parallel with 341 to provide
ample capacity for their duty which is to minimize pressure increase
caused by rapid inflow of oil compressing the gas confined within
an elastomer bag inside the steel chambers of the accumulators;
this construction is a spring with an extremely low spring rate
as compared to coiled steel springs, and coil springs have a very
limited travel before their coils contact together. However, a cylinder-piston
design can be of any useful travel if the accumulators are of adequate
capacity. Both accumulators are connected to manifold tubes 293;
vertical tubes 290 conduct pressurized oil from 293 to the tops
of the hydraulic cylinders 275; this makes the cylinders of the
pull design. Hook shaped members 281 are connected to hydraulic
cylinders 275. Columns 298 transfer the thrust of 290s into the
main frame 1-MF, because 290s have slip connections at each of their
ends and therefore act like pistons. The object of this new concept
is to provide extremely rapid and easy removal of the bowl assembly
1-BA from the main frame; two workers can release the accumulator
pressure and tilt the swing hooks and cylinders clear of the flange
of 1-BA and attach lifting cables and a crane with an operator can
have the bowl assembly sitting on the ground within twenty minutes;
other designs common in cone crushers require several man hours
to remove large nuts and nut locking devises plus careful guidance
by several men when lifting their bowl assembly over many large
threaded rods and repeating such care at reassembly. For example:
our new unique system enables two men plus a crane operator to remove
the bowl assembly from the main frame, remove worn mantle and bowl
liner, replace with new, pour backing epoxy, and fully reassemble
within three hours in the more popular mid size crushers; no other
cone crusher can closely match this. When down time is factored
in of such costly operations as rock plants are, the cost savings
of our design are enormous! 24 is a lube oil drain to a reservoir
not shown; 224 is one of several stop blocks that resist the torque
of depending arms 222. In cone type crushers there is a main frame,
and resting upon it is a removable bowl assembly that is designed
to lift when uncrushable objects enter the crushing chamber; also
there is a tendency for the bowl to "float" slightly during
very severe crushing; these actions causes the bowl assembly to
try to creep relative to the main frame; this can not be permitted,
hence the anti-rotation stops; usually there is wear between anti-rotation
stops with all makes of cone crushers, with our design 224 is reversible
and 222 can be removed, repaired with weld metal, and reattached;
this can also be done with 224. Pressures in GAS over OIL design
are adjusted to resist lifting of the bowl assembly when crushing
rock but to allow lift by uncrushable objects; Louis Johnson, co-inventor
of this application, is the original inventor of combining accumulators
with hydraulics for rock crusher protection systems; see Johnson
U.S. Pat. No. 3118623 and U.S. Pat. No. 4192472. 1-BA is a bowl
assembly that contains a rotatable member to which is attached 243
adjustment ring; 326 is one of two opposed power adjusters that
rotate 243 when activated the crusher product is sized as desired.
FIG. 2 shows the main frame with bowl assembly removed; hooks 281
and cylinders 275 are tilted outward to their stop positions thereby
providing ample clearances for lifting the entire bowl assembly;
218 is a hard steel V-ring pressed into the top of the main frame,
and upon which bowl nut 220 seats, FIG. 1; 119 is a wear mantle
seated on a cone-head and retained by a combined hydraulic piston
and cap screw unit; 342 is one of three lifting brackets; 276 are
links that connect 275 to 294 and allow limited tilting of 275.
FIG. 3 is vertical section view taken through the gear train; it
shows how most of the parts fit together; the numerous numbers are
required to point out all the new concepts of our invention as well
as those parts that are not new art but essential to assist in understanding
our machine; 331 braces the wall 1-W to maintain the exact spacing
between 1-W and plate 4 and to prevent any erosion of bearing housing
156 by falling rock; 263 is a sectioned wear liner that protects
wall 1-W from rock erosion and is held by bolts for easy replacement;
333 is a large socket head cap screw that holds wear cap 122 which
protects 99 a conical headed cap screw; FIG. 30 details said concepts.
Other numbers are detailed in the following pages.
FIG. 4 is a plan view of lower section of the main frame; 2 are
full depth crossbeams spanning across the inside diameter of 1-W
less the thickness of endplates number 3 the outer faces of which
are machined to the same radius as 1-W's inside diameter; beams
2 are configured to have near uniform strength across their lengths;
one beam is full length with two half length beams minus thickness
of first beam forming the other beam; all said beams are prep machined
including drains 35 before being fully welded together to form a
90.degree. X frame; the central top faces of said beams are machined
flat and square to the vertical centerline of said main frame; members
8 each are blind threaded to receive cap screws and are then positioned
and welded to each side of beams 2 in all four quadrants; arcuated
members 6 are premachined prior to being positioned at the same
radius through three quadrants; the bottom faces of 8 and 6 are
on the same plane; members 4 and two 5s form a support for a bevel
gear housing. All members forming said quadrants are fully welded
before the upper faces of members 4 5 and 6 are face machined
simultaneously with beams 2 with all in the same plane; the radius
of members 3 are machined concentric to the frame's axis and to
the same radius as the inside diameter of wall 1-W, and lower ends
are machined 90.degree. to centerline and to an exact distance below
the top faces of beams 2; cover plates 20 are attached to 8 and
6 with gaskets between by cap screws at final assembly of a complete
machine. Member 10 is fully machined before welding; pin 12 is inserted
at its center before it engages hole 12-H which centers 10 on beams
2; bore 21 in member 10 FIG. 7; 10 is positioned precisely with
a gage over bore 23 in plate 7; 10 is welded to 2s at specified
places and fully welded to 4 5 and 6; welding is accessible through
the openings that will be closed by covers 20; this procedure forms
four oil tight chambers and adds strength and stiffness to beams
2 and saves time and costs of vertically machining the two bores
later and premachines parts that are inaccessible after assembly.
After this procedure is complete, the assembly is positioned on
base flange 1-BF and secured with welds; cylinderical wall, 1-W,
is a rolled steel plate without its ends joined; it is wrapped around
said assembly with one end centered on one end plate 3; 1-W is forced
to match a circular score line etched into 1-BF when it was premachined
and is tack welded as necessary when being positioned through 360.degree.;
its joining gap is then welded about the height of member 3. A top
flange 1-TF, FIG. 3 is machined to an inside diameter equal to
the outside diameter of members 3 plus two wall thickness of 1-W,
and the outside diameter is oversized, and one side is faced with
a small chamfer at its inside diameter, and 1-W has a small hand
ground chamfer at its outer top edge to facilitate said flange to
being forced over said wall to an exact distance above 1-BF; both
are skip welded as 1-W is forced against 1-TF free of any gaps;
anchor plates 294 FIGS. 3 and 41 are positioned and partially
welded. The whole assembly is now ready for complete welding; after
which the top inside diameter of 1-W and top face of 1-TF and its
O.D. are machined to specific dimensions. Any top face warpage to
10 by welding is corrected by machining at this time. Upright members
9 are supports for shield 336 FIG. 3. FIG. 5 is a vertical sectioned
taken through B B'; it shows the full depth of beams 2 the frontal
position of members 4 and 5 with precision bore 22 that supports
a pinion shaft housing 156 oil drains 24 and 35 and the position
of member 7 that serves both as a cover and support for a bearing
housing, bearing, a vertical shaft with a bevel gear attached, and
the separating forces of the bevel gear. Arrows show where member
10 will be placed. A cutaway in the 2.sup.nd quadrant shows the
end of a member 11 within a member 6 and oil holes drilled through
11.
FIG. 6 is a vertical sectioned view of member 10 taken through
C C' FIG. 7. 10 is a steel plate of substantial thickness to cope
with severe stresses and to provide adequate depth for recess 28
and threaded holes 19 and for the width of a roller bearing in bore
21; 32 is an annular positive angled shoulder over which is shrunk
fit a seal ring spacer. FIG. 7 is a plan view that details member
10's construction before welding to beams 2 and arcuated members
6. The top face of member 10 is recessed at 28 to exact inner and
outer diameters to match a press fit to member 38 FIG. 12 a spindle;
the walls of 28 absorb huge shearing stresses; multiple holes 19
are precision drilled and threaded for large cap screws to pull
said spindle tightly against the bottom face of recess 28; bore
21 is precision bored an exact distance from center for accurate
gear meshing; a roller bearing seats in this bore; holes 17 with
recesses 16 FIG. 8 are precisely positioned as are holes, 33 34
25 and 26 to match holes in said spindle; 30 is a gear inspection
hole; FIG. 9 is an enlarged section of groove 27 an annular recess
to divert oil to drains 18 and a boss for positioning member 13;
multiple drain holes 18 are positioned to avoid being obstructed
by beams 2; hole 12-H is drilled on center to accurately position
member 10; boss 32 is machined to hold a seal spacer; the bottom
surface of member 10 is faced, and holes 17 25 26 33 34 and
for nozzle 15 are threaded; hole 142 is drilled after the base frame
is virtually completed. FIG. 9 details 13 a lube oil deflecter to
channel oil to drains 18. NOTE number 18 is used at several places
and FIGs to represent oil drains. FIG. 10 details 14 an oil trap
to force lube oil into nozzle 15 that ejects lube oil just ahead
of the meshing of gears 126 and 127.
FIGS. 11 &12 shows a spindle 38 that is force fit into recess
28 in member 10 by multiple cap screws. This construction accommodates
both shearing and tipping forces that are huge in cone crushers,
and because it is secured by cap screws and extracted by jack screws,
this spindle is easy to service or be replaced by a new one even
as the main frame remains in its working position. Other makes of
cone crushers that use an embedded post shaft design have extreme
difficulties to extract its shaft because of the very tight shrink
or press fits extending through the full depth of their center member
as such designs require, and such machines must be removed and be
hauled to a repair shop if their post shaft must be replaced, all
of which is very costly and time consuming. Except for the crusher
design of this patent application all other cone type crushers whether
post shafted or open for an eccentric mechanism have massive deep
and wide annular center sections cast integral with radial arms
and are recessed to accommodate a large bevel gear; these crushers
must be built as such to resist deflecting cycling forces which
cannot be totally contained; such construction adds substantially
to the weight and costs of those machines. Such stresses and deflections
do not transfer into our bearing design. FIG. 12 shows the conical
construction, 43 of our new concept design that has a cross-sectioned
area at dimension and a smaller cross-sectioned area at '; subtracting
area at ' from area at gives an area equal to an area in a plane
of the same outside and inside diameters. We use this as a thrust
bearing area. A cylindrical extension 48 of ' diameter stabilizes
an eccentric member, 65 FIG. 18 when the hydrostatic oil film between
the conical surfaces is too thick. The area difference of minus
is substantial enough to provide an adequate hydrostatic thrust
bearing when lube oil under pressure is injected into flutes 42
and between bearing surfaces; the conical shape is large enough
to eliminate diametral clamping by thermal shrinkage of metals of
different coefficients of expansion, a severe problem with straight
shafted crushers that use bronze bushings, because such bushings
are heated by friction and try to expand against a much stronger
steel or iron housing which is cooler and has a lower coefficient
of expansion by a factor of about 60%; the results are the bushings
are compressed, and when the crushers are shut down and bushings
cool, they shrink to a smaller diameter and would clamp and seize
to shafts they work against; the only way such crushers can cope
with this phenomenon is to have excessive bearing clearances larger
than the amount of shrinkage, but this in turn greatly reduces radial
bearing area caused by diverging arcs and also causes inaccurate
meshing of bevel gear drives, because the larger gear orbits true
center by whatever the extra clearance may be which causes reverse
end loading of the gear teeth during every 180.degree. s of rotation.
Also constant shrinking and expanding between operating and shut
down of the machine causes myriads of tiny cracks in the bushings
that resemble a dried mud flat; the oil film is disrupted adversely
affecting lubrication. Our one piece design sans bushings permits
a nearly uniform oil film thickness through 360.degree. because
any differences of expansion between dissimilar metals is accommodated
by the eccentric member lowering on the tapers if it expands, and
if it shrinks, it climbs relative to the spindle on which it runs;
while the eccentric loading may force a slight difference in oil
film thickness to absolute true running, it is of no consequences,
because our eccentric gear's teeth are parallel to its axis, vertical
movements and meshing clearances accommodate any slight changes
in depth of meshing. With its hydrostatic lubrication our bearing
finds its bearing clearances in proportion to the imposed loads;
injected oil is at a volume and pressures that prevents metal to
metal contact; the results are running accuracies comparable to
roller bearings, with very low friction and wear and not subject
to cracking as with bushings nor fatigue spalling as are roller
bearings. Original and maintenance costs are substantially less
with our design. However, our hydrostatic bearings were not without
fault; when operating unloaded, a surplus of oil and varying viscosities
caused too thick an oil film which created instability to the eccentric
and cone head; after extensive testing we corrected the problem
by adding the short cylinderical sections, 48 FIG. 12 at the top
portion of the spindle to stabilizes the eccentric and cone head
75 FIG. 3 and FIG. 27. FIG. 11' is a plan view of the top of said
spindle; 40 is a bolting flange; 41 are multiple countersunk holes
for large socket head cap screws; 43 is a conical super accurate
smooth surface its full length; 39 are two annular grooves that
deliver lube oil to holes rotating with an eccentric member 65;
said grooves are detailed in FIG. 13 with oil holes 55; tubes 50
with seals 51 transfer hydrostatic lube oil across a shimming space
163 between said spindle and a thrust bearing body, 160 FIG. 33;
49 are spaced apart annular grooves around extension 48 to supply
hydrostatic lubrication between the bearing surface of 48 and eccentric
member 65; 44 are three equally spaced smooth wall holes for tubes
50; 45 are threaded holes for retaining said thrust bearing; 46
are multiple threaded holes for retaining a tubular chamber 158
FIG. 33; 47 is a chamber enclosing a spur gear. Surfaces 43 and
48 are machined to near zero tolerances and extremely smooth finishes;
the fluting 42 in the spindle is evenly spaced above and below the
annular galleries 39. Oil volume is proportional between to the
areas of the two zones, but is equalized to each flute by flow dividers;
lube oil is supplied at whatever pressures and volume required;
the varying loads of crushing vary the operating clearances, and
the escape rate of oil at the ends of each bearing is similar to
a variable valve, but at some point of clearance the escape rate
reaches a limit that prevents further restrictions of closure because
the pump pressures are always greater than crushing pressures, and
volume is virtually constant. Our research has not revealed that
a unidirectional conical hydrostatic bearing capable of coping with
simultaneous radial and thrust loading has ever been used before
in any kind of a machine. A thrust bearing positioned on top of
said spindle is held in place by a slight press fit in bore 56 FIG.
16 and by cap screws threaded into holes 45; FIG. 14 details tubes
50 sealed by O-rings 51 that transfer lube oil across the space
between the spindle and thrust bearing providing hydrostatic lubrication
from gun drilled holes from the base of 38 to holes 44 which transfer
oil to tubes 50.
FIG. 16 shows a vertically sectioned view of said spindle an alloyed
steel casting capable of being cryogenically hardened after machining;
61 is an as cast hollow chamber with an inlet 53 designed to swirl
incoming fluid, and an overflow outlet 62 designed to flow a heating/coolant
fluid through said chamber thereby heating or cooling the actuating
members of the machine as local weather temperatures and operating
temperatures may require, and to help keep lube oil at an optimum
viscosity range; heating or cooling from the inside out is more
efficient, safer and simpler than flame heating the outside of the
gyrating assembly as is done when other cone crushers are shut down
between shifts in very cold weather, and heating or cooling lube
oil is done within an exterior tank. Said fluid flows through a
heating unit or through a fan cooled radiator, or in extremely hot
climates a chiller maybe needed before said fluid enters cavity
61; 52 are gun drilled holes to conduct lube oil to each designated
flute 42 and to thrust bearing 160 some of which is shared with
grooves 49; 56 is a precision bored recess for a tight fit with
thrust bearing body 160; 57 is a fluid tight tubular member to enclose
a hydraulic motor 167 FIG. 33; 58 is a solid disc cover with a sealing
ring 59 and is retained in place by ring 60 that engages a groove;
an option is to weld 58 fluid tight; its purpose is to prevent heating/cooling
fluid from mixing with lube oil; oil lines and heating/cooling lines
from members 11 connect to designated connections in member 10;
holes 17 align to holes 52 and hole 33 aligns to hole 55 and hole
34 aligns to other hole 55; holes 52 and 55 carry lube oil; holes
53 and 54 carry a water antifreeze mix; all said holes are sealed
with elastomer seals in recesses 16. Holes 52 deliver lube oil in
equal volume to designated flutes in said spindle 38 to lift and
lubricate eccentric 65 and to the thrust bearing less what goes
to grooves 49; oil holes 55 FIG. 17 deliver lube oil to annular
grooves 39 that continually supply lube oil to holes 68 through
eccentric member 65 as it rotates around the spindle, page 8 FIGS.
18 and 20 to lubricate the conical bearing surface 81 of cone head
75 and matching surface of eccentric 65. Hole 53 delivers and swirls
heating/coolant fluid to chamber 61 within said spindle, and tube
62 withdraws it near the top of said chamber; this insures a full
chamber of agitated fluid.
FIG. 18 show a vertical exterior view of the eccentric member 65
which is a non-ferrous bearing quality casting; the taper of outer
conical surface FIG. 18 is an exact match to the taper 81 of cone
head member 75 FIG. 29; 64 is a cylinderical extension having two
spaced apart bearing arcs, A-1 and A-2 and in between arcs of X
radius. Because it is not possible to use flow dividers to control
oil flow to the outer bearing surface, we use exchangeable nozzles
69 FIGS. 19 & 20 and detailed in FIG. 21 to vary the hole sizes
to force the oil volume as best served, the eccentric offset through
180.degree.; said nozzles, usually pipe plugs drilled through, have
tapered threads and are positioned at the exit of each hole 68 whose
inner ends center on grooves 39; holes feeding lower flutes 66 rotate
around the lower groove 39; upper flutes receive oil from the top
groove 39; lube oil that ejects out of the top of the spindle and
out of the thrust bearing 160 works again as it passes between the
bearing surface of eccentric 65 and 81 of member 75; open ended
valleys 67 drain lube oil to prevent pressure build-up in the space
above the eccentric, because hydrostatic bearings must discharge
lube oil into low or zero pressure conditions to perform as intended.
The eccentric does not contain bushings; it is a one piece member
and has four bearing surfaces, two conical and two cylindrical;
FIG. 19 a plan view, has an inside diameter, 63 FIG. 22 with just
enough diametral clearances for oil film and thermal contraction
to rotate freely around extension 48 of spindle 38; outer bearing
diameters of extension 64 have arc A-1 of less than 180.degree.
and a spaced apart arc A-2 that have minimal operating clearance
co-acting with bearing surface 82 in FIG. 29; said arcs are equally
centered to the plane of the eccentric; radii X form large arcs
between arcs A-1 and A-2 and have substantially shorter radii which
form very large clearances that can absorb excessive thermal expansion
should it occur by bulging radially enough to eliminate clamping
against surface 82 FIG. 29; the eccentric metal is flexible enough
to allow said bulging without excessive bearing pressures on arcs
A-1 and A-2. The conical angles of FIG. 18 and cone head, FIG.
29 are held concentric to their centerlines as is a spherical thrust
bearing 106 to said spindle FIG. 30 and 160 FIG. 33.
FIG. 22 is a vertical section view 90.degree. to the plane through
the eccentric offset. 73 is the inner conical bearing surface that
rotates about spindle member 38 concentric to centerline 101 as
does cylinderical bore 63. 72 is a annular groove that accepts hydrostatic
oil that escapes from the top of the taper 73 and funnels the oil
outward through holes 72-H to prevent back pressure from the close
fit of cylindrical bearing 63. Discharged oil exits just ahead of
arcs A-1 and A-2 for additional lubrication. 102 is the centerline
of the outer cone and bearing extension 64 and is canted by angle
.alpha. which establishes the radius of gyration of cone-head 75.
66 is a profile view of a typical lubricating flute with a nozzle
69 in a hole 68 positioned to receive oil from the upper annular
groove 39; the cutout section shows a 69 receiving oil from the
lower 39. Keyways 70 and keys 77 FIGS. 24 and 25 transfer driving
torque and accommodate thermal expansion and contraction without
distorting eccentric member 65; cap screws holding 65 to an eccentric
drive plate, 150 FIGS. 24 and 25 have sufficient clearances in
holes 192 to accommodate differential thermal movements of said
eccentric. 74 centers eccentric 65 on its drive plate 150. FIG.
23 is a bottom view showing the normal positions of keyways 70 and
threaded holes on R-5 radius, also shown are holes 68 exiting the
conical inner surface.
FIG. 24 is a plan view of the eccentric drive plate 150; it is
attached to said eccentric 65 by cap screws in holes 192 drilled
on R-5 radius and is driven by keys 77 FIG. 25; radii R-2 R-3
and R-4 are centered on the main centerline of the machine; R-1
is a varying radius from centerline 102 that reaches its maximum
at the largest conical diameter of eccentric member 65 and diminishes
to zero at apex 100; 104 are threaded holes for attaching counterweights;
FIG. 25 is vertical sectioned view of member 150 showing partial
assembly with 130 an internal tooth gear that drives the eccentric
member; it is attached to the underside of 150 by multiple cap screws
and is shouldered to run concentric to main centerline 101; a section
of 36 a labyrinth dust seal seated against shoulder 80 is shown;
it is concentric to 101. 18 are oil drains that flow lube oil back
to a reservoir. The combined weights of the cone head 75 mantle
119 FIG. 27 and part of the eccentric establish a center of gravity
that when gyrating eccentrically creates centripetal forces that
must be neutralized; this is done by counterweighting; the extended
R-4 radius provides about half the required counterweight, and most
of the extra weight required is provided by weights 151 FIG. 3 and
fine tuned by weights 152 (see FIG. 32) that can be changed without
removing the cone head. Pins 155 embedded in holes with clamping
washers 399 plus long cap screws in threaded holes 72 hold all upper
counterweights against centrifugal forces. The spinning counterweights
generate considerable air turbulence within the open chamber below
the cone head; circular shields, 336 FIG. 3 supported on upright
members 9 FIGS. 4 and 5 direct air flow upward and downward rather
than radial; this reduces rock dust erosion of the counterweights
and directs some air flow into cavities 79 of said cone head member
thereby producing some cooling effect to it. 80 is a positive angled
boss to retain seal 36 by shrink fit
FIG. 26 is a segmented plan view of the top of the cone head; FIG.
27 shows a vertical view of the exterior configuration of the cone
head 75 this is the member that is gyrated by the eccentric and
performs the crushing action; 119 is a wear mantle that is firmly
clamped, detailed on FIG. 22 to said cone head and prevents wear
on the cone head itself. Depending on the abrasive characteristics
of the rock being crushed, the wear life of 119 can be from a few
days to years. Because of the extreme difficulty to machine the
wear material, usually manganese steel, we choose to employ a fairly
narrow machined surface 76 to support the mantle at its rim this
leaves a space inward that is filled with a liquid epoxy backing,
FIG. 22 that hardens in a short time; 80 is a boss for retaining
a sealing ring; FIG. 28 is a plan view of the bottom; 78 are struts
that transfer crushing forces into the conical wall of bearing surface
81 FIG. 29; 79 are spaces between said struts to reduce weight,
costs, and make easier to counterbalance; 84 are threaded holes
to retain a conical thrust bearing; 86 are two or more holes evenly
spaced in conical surface 85 we prefer using three, that lock a
piston from rotating; 87 is a precision bore that serves as a cylinder.
FIG. 29 shows a vertical sectioned view of said cone head; 81 is
an extremely accurate conical and smooth bearing surface that journals
on the eccentric 65; 91 is an extension of the cone head that serves
as an oil deflecter and a protection of surface 81; 82 is a smooth
bore cylindrical bearing surface that co-acts with the eccentric's
bearing surface 64 FIG. 22 to stabilize the conical hydrostatic
bearing section below; 89 provides gyrating space around thrust
bearing 160 FIG. 33; 83 is a precision recess to retain 106 FIG.
30 page 13 the convex half of thrust bearing 160; 92 is a short
steep taper to assist the installation of a large elastomer seal
ring; 88 is a smooth cylindrical bore in which a piston slides;
85 is a conical surface to match the top conical surface of a piston;
86 are clearance holes for pins 97 FIG. 30; 90 is a seal ring groove,
and 87 is a smooth bore for a piston extension to slide.
FIG. 30 details the assembly and functions of parts that retain
said mantle 119 and comprise one of the most important elements
of our invention and claims. Piston 93 combines a mild steel disk
having a steep tapered female buttress thread into which a very
high strength steel cylindrical member 94 is assembled with an anaerobic
sealant and tightened to refusal; 94 has an internal thread that
accepts the male thread of cap screw 99 with a free fit; the wall
thickness of 94 provides more tensile strength than 99 in case a
breakage should occur; 94 has a valve assembly 110 threaded into
the recessed face of its threaded bore; a hole 118 is angle drilled
from above the first thread of its taper into the hole containing
110. Seals 95 and 96 provide leak proof retention of high viscosity
oil that is pumped into the space between said seals. When installing
a new mantle it is lifted by a crane or other means and preferably
using our safe lift device (U.S. Pat. No. 5323976) and placed
over and centered on cone head 75; said lifting device is removed,
and conical washer 98 is positioned; large cap screw 99 having a
double conical head is threaded into 94 and hand tightened with
a pin wrench to pull piston to face to face contact of its angled
surface. FIG. 31 is an enlarge sectioned view of 110; an oil pump
extension 121 engages fitting 117 through a threaded hole in 99;
pumped oil flows past ball valve 111 and out hollow hex screw 113;
cap screw 116 is slightly loose until all air is ejected, then it
is tightened forcing ball valve 114 to be firmly seated; oil is
then pumped into 117 until the piston is pulling between 200K and
800K lb.s depending on the size of the crusher; these forces are
easily obtained with our new system but extremely difficult with
sledging against a wrench to turn the screw or nut as in all other
designs. Epoxy backing 120 is poured through holes cast near the
top of the mantle During crushing the mantles on every kind of gyrating
crushers tend expand due to pressures of crushing; this phenomenon
causes the mantle to creep relative to its cone head in the direction
the cone head gyrates; this results in the cap screw or nut, whichever
is used, becoming so tight that it is impossible to unscrew; the
hand of the threads are determined by the direction the cone-head
gyrates at time of manufacture of the machine, so that it will continue
to tighten, if the threads were the other hand the mantle would
loosen which could have disastrous results, consequently a cutting
torch is necessary to relieve the enormous pressure and friction;
either a torch ring is used, or the washer is cut, which then another
must be purchased, or the mantle is cut with an arc-air electrode
because manganese steel cannot be cut with gas torches; these are
time consuming and costly methods that have been and still are unavoidable
until now. To prevent the piston from turning with its cap screw
in our new concept we use pins 97 pressed into the piston and engaging
clearance holes 86; when mantle changing time comes, wear cap 122
that has been held in place by a cap screw 333 is removed, and a
small socket wrench on an extension handle opens screw 116; oil
pressure is releaved through port 115; the cap screw 99 can be unscrewed
with a hand wrench; the work is easy; the time is fast, and nothing
has been destroyed. However, nothing mechanical is fool proof, and
should the hydraulic oil escape from its containment the cap screw
will draw the piston tightly against surface 85; in that event washer
98 can serve as a torch ring; copper washer 105 prevents a cutting
torch flame from damaging the surface of the cone head, because
copper can't be cut by a cutting torch. Nut 334 was left in place
at time of assembly to enable our safe lifting device to be reattached
and used to lift off the worn mantle; a setscrew that was threaded
into said nut at the time of installing a new mantle to protect
the nut from filling with epoxy and later by rock dust must be removed
first. Other members of FIG. 30 are thrust bearing 106 having a
case hardened and polished spherical surface on a radius centered
at apex 100 and is retained in recess 83 by cap screws 107. A universal
joint 108 in a recess is held by cap screws; 109 is one half of
a jaw clutch fastened to said joint 108; its conical projection
is to guide said clutch into its mating half which is a blind assembly
in an inaccessible position; these are parts of a cone-head anti-spin
device FIGS. 33 and 34.
FIG. 32 shows vertical sectioned layout of our double reduction
gear train; 125 is the powered input pinion shaft; it is journalled
in tapered roller bearings 131 in tubular housing 156; 134 is mechanism
to adjust said bearings to correct operating clearance; 138 is a
sealing means against entry of contaminants and escape of lube oil;
139 is a replacible wear band to protect the shaft from a rubbing
seal; 329 is a cover plate retaining said seal; 126 is a spiral
bevel pinion gear keyed and shrunk fit to said shaft; 137 is elastomer
seal ring to seal against oil loss; 142 is a passage way in combination
with dike 145 to deliver lube oil to outer bearing 131; a small
drain tube drains this oil to main oil drain 24; 136 are shims for
adjusting pinion gear mesh with mating gear 127; 128 is a vertical
shaft with spur gear 129 preferably made integral but could be a
separate gear keyed and shrunk fitted to shaft 128; roller bearing
133 flinger 141 and spacer collar 140 position gear 127 to an
exact position from gear 129 and ball bearing 132; by positioning
bevel gear 127 above bevel pinion gear 126 the torque pressure on
127 and counter torque on spur gear 129 greatly reduces the loading
on bearings 133 and 132; the radial loading on inner bearing 131
adjacent to gear 126 would be the same regardless of rotation direction;
bearing 132 is capable of handling thrust loads in either direction
as well as radial loads; it is retained in fixed position in housing
135 by retaining plate 143 and cap screws; lock washer and nut 134
hold 132 firmly against the shoulder of shaft 128; 136 are adjusting
shims for gear 127 meshing with 126; both gears require meshing
adjustability; this system insures obtaining and maintaining proper
bevel gear meshing; spur gear 129 does not require meshing adjustment;
gear 130 is attached to eccentric drive plate 150 which in turn
is attached to eccentric 65 as previously shown in FIG. 25; when
lube oil enters between said eccentric and spindle 38 the eccentric
assembly lifts to a level that balances the oil escape rate to the
weight of the assembly; oil viscosity is also a factor; when the
pressures of crushing begin, the assembly is forced down to a thin
oil film; total variations of vertical movement between running
empty to maximum loading may reach two millimeters; straight tooth
gears accommodate these variations; any radial runout is accomodated
by extra depth cut into these gears. FIG. 32 also shows labyrinth
seals 36 seal spacer 37 counterweights 151 air spaces 153 for
rock dust to escape thereby minimizing dust from build-up on the
inside surfaces of the weights, spacers 154 and fine tuning balancing
weights 152. A very important advantage of this design is its elimination
of the massive gear well of other cone crushers and permits the
use of full depth crossbeams for greater strength with a substantial
reduction in weight and costs, especially so because structural
steel is about 30% the cost of cast steel and much less subject
to flaws. 18 are oil drains; 35 are drain ports in beams 2.
FIG. 33 is a vertical sectioned view of the thrust bearing 160
and cone head braking mechanism; 161 is a bearing quality over-lay
of bronze welded to steel member 160; however, such over-lay could
be other bearing quality metals e.g. Babbitt or hard plastics. 164
are radial lube oil grooves spaced apart by closed ends and are
supplied with oil by tubes 50 with sealing rings which transfer
hydrostatic lube oil across a shimming gap between spindle 38 and
member 160; cap screws 162 pull member 160 into a tight fit in recess
56 and to hold same; jack screws 165 are used in adjusting shims
163 and to extract 160. The thrust bearing is positioned vertically
to support the cone head a predetermined distance above the eccentric;
this distance is the sum of the sines of the desired oil film thickness
of the spindle angle and the outer angle of the eccentric. The lubrication
of the cone head conical surface 81 is mostly hydrodynamic, but
is assisted with some hydrostatic lift. When cone crushers are running
idle (not crushing), the cone head will tend to spin with the eccentric
because of frictional drag; this is undesirable; Louis Johnson,
co-patentee of this application, invented the first head brake for
cone crushers, U.S. Pat. No. 3207449 in which he used an over-running
clutch, and which others have copied; the problem with such clutches
is they cannot endure shock reversing impact nor torque loads above
their capacity; when this happens they rupture or shearing devices
are used to prevent rupture; such clutches are expensive to buy
and more costly to replace. Our new concept uses a hydraulic motor
167 with a valving mechanism that permits free turning in one direction
but resist turning in the opposite direction; an enlarged view of
the valve FIG. 34 details its operation; when crushing the cone
head turns slowly retrograde to the eccentric and must not be restrained.
To allow turning freely oil is drawn in through valve seat 180 and
around ball valve 181; a stop pin 182 limits the travel of 181;
oil flows through passage way 184 and into the motor through port
185 and out the motor through port 189 but when bearing friction
tends to turn the cone-head with the eccentric oil is then drawn
in through port 189 and ball valve 181 closes; for oil to escape
it must force ball valve 186 to open which compresses spring 187;
bypassed oil can be vented through hole 194 or through hollow hex
screw 188 which is drilled to exhaust oil; the screw adjusts the
spring force to just enough resistance to override head drag, but
not enough to permit harm to co-operative parts if somehow the cone
head adheres to the eccentric; to machine passage way 184 it is
necessary to have an opening which is closed later with weldment
183; cap screws 379 hold valve body 168 oil tight to motor's porting
face. At assembly of cone head to the thrust bearing and eccentric
which is a blind assembling procedure, jaw clutch cone 109 automatically
finds alignment to female cone 174 and slides into it, but it is
unlikely that the projecting lugs of 174 will find slots 193 in
cone 109 initially in which case spring 173 yields and spline 172
slides on 171 as needed; after the cone head is fully in place,
and the lube oil pump is started, the head is easily turned by hand
in the drag direction, thereby finding alignment where spring 173
will push the jaw clutch to full engagement; the universal joints
convert eccentric rotation to inline rotation; The motor is suspended
by tubular member 158 which is torque restrained by cap screws 159;
fluid tight enclosure 57 prevents intrusion of heating/cooling fluid;
lube oil escaping inward from said thrust bearing 160 fills the
enclosure 57 and motor mount 158 through port 191 to the level of
port 166; any air in the enclosure vents out hole 190 and 166; any
excessive pressure is relieved through hole 166 and valleys 67.
FIG. 35 shows how the lube oil flows in our hydrostatic design;
200 is a flow divider that apportions oil equally to the flutes
42 in the lower zone of spindle 38; said oil flows out of 200 into
tubes 204 into members 11 on each side of beam 2 and into three
chambers formed by members 6 10 and 20; members 11 are flat bars
of steel of ample sizes to protect oil passage ways drilled through
them from the ravages of falling rock; wear caps 335 FIG. 3 further
protect members 11 and beams 2. Flow divider 201 equally apportions
oil to the upper zone of said spindle and also to the thrust bearing
160 through lines 205; proportionator 203 ratios the oil to annular
grooves 39 through lines 206 and 207; both lines deliver their
oil to their pair of members 11; the lower groove gets the larger
portion of oil from 203 because it supplies a larger bearing area;
multiple lines within said chambers conduct their portions to specific
connections in member 10; return oil drains through holes 18 in
10 into all four chambers, then through ports 35 in beams 2 and
out exit port 24 to a tank not shown; lube oil drawn from said tank
passes through filters and heat exchangers before reentering the
machine; a three chambered pump supplies oil to connectors 195
196 and 197. Heating/coolant fluid normally water and antifreeze
mix enters through 208 and out 209 after circulating within chamber
61; said fluid also passes through heat exchangers as it circulates
through the system. Numbers 292 293 295 are members of the safety
relief system.
FIG. 36 A machine that crushes rock by compression has a stationary
member and a moving member to form a squeezing force; in a cone
crusher the stationary member is called a bowl which in this patent
application is number 240; multiple gussets 245 brace the conical
wall of 240; 246 are open spaces between said gussets. To protect
the bowl from wear a bowl liner 265 a casting of wear resistant
metal, is positioned in the bowl where it seats on conical surface
267; to retain it in place, we have designed a sliding wedging system
using three or more wedges 250 evenly spaced circumferentially and
to bear against an inverted conical flange machined at the top of
said liner; FIG. 37 is a plan view through section G G' that details
their construction: thrust bolts 254 are locked from turning by
vertical slots 257 as thrust wedges 250 are forced inward as nuts
255 are turned; blocks 253 absorbs the thrust, and washers 256 protect
253 from wear of turning said nuts; cap screws 252 and cover plates
251 prevent wedges from tipping and are tightened after all wedges
are tight; slots 259 provide travel of wedges relative to cap screws;
rectangular plate washers 251 are constructed to always cover said
slots to prevent debris from entering slots; 258 are guides to prevent
skewing of wedges; 266 is a wedging ramp with a conical radius to
match liner's. When changing liners the bowl assembly is removed
from the base frame as previously explained; the hopper is unbolted
and l |