Abstrict A rock crusher of the gyratory cone type having a mainframe structured
to be exceptionally strong yet lighter and less costly to manufacture.
A tapered spindle bolted to mainframe, is drilled with multiple
oil holes, is hollow for circulating heating/cooling fluid, and
supports an adjustable thrust bearing. An eccentric member journals
on spindle; eccentric has outer taper offset and canted relative
to inner taper, and each taper has concentric cylinderical extensions;
A gyrating conical member journals on eccentric. Said thrust bearing
having spherical surfaces supports conical member on said spindle.
A double reduction gear train transfers power to eccentric. Flow
dividers direct lubricant to specific multiple ports for hydrostatic
lubrication to conical and thrust bearings. Counterbalancing means.
A detachable top frame positioned on top of mainframe is restrained
against radial and circular movement. Pivoting hooks and hydraulic
cylinders tilt outward facilitating rapid servicing. Gas accumulators
with hooks and cylinders restrain top frame against crushing forces,
yield to non-crushable objects. Detachable top frame has internal
thread engaging an external thread of a rotatable member that when
rotated adjusts for product sizes and replacement of wear parts;
a means to lubricate said threads. Power means to unlock, rotate,
and lock said rotatable member. A wear resistant mantle is clamped
to gyrating conical member by hydraulic means. A wear resistant
liner is held in rotatable member by slidable wedges.
Claims Having thus described our invention, we claim:
1: In a crusher of the gyrating cone type a main frame formed by
a circular wall of rolled steel plate having bottom and top flanges,
and crossmembers forming a 90.degree. shape; a base plate joined
to said crossmembers and centered to the vertex of centerlines of
said two crossmembers, three chambers under said base plate in three
quadrants and welded securely and leak proof to the base plate and
sides of said crossmembers; removable covers at the bottom of said
chambers and oil passages through said crossmembers joining chambers
for lubricant drainage. A chamber in the first quadrant formed to
contain a vertical gear shaft with a bevel gear keyed and spaced
on said shaft; the top end of said shaft having a spur gear either
integral to shaft or keyed to said shaft; a roller bearing, an oil
slinger, and a spacing collar between said spur gear and said bevel
gear; said roller bearing is housed within said base plate member
that is welded to said two crossbeams; the lower end of said shaft
is journalled in an anti-friction bearing that can assume both radial
loading and thrust loading in both directions; a means for adjusting
the vertical position of said bevel gear. A bevel gear on a horizontal
shaft meshes with said gear on said vertical shaft; said horizontal
shaft is journalled on two spaced apart roller bearings; said bearings
and shaft are positioned within a tubular housing that extends through
the wall of said main frame and into said chamber in the first quadrant.
An adjustment means to position said housing to obtain proper gear
meshing; said housing is flanged for bolting to said main frame
and is sealed against entry of contaminants; said horizontal shaft
extends for attaching a power driving means. An exchangeable seating
ring pressed into the top opening of said main frame. Spaced apart
plates extending radially outside the main frame wall and welded
to the top face of the bottom flange and as far vertically as the
height of said plates. Said plates drilled to pass hydraulic fluid,
drilled for retaining header plates for hydraulic tubes, and for
anchoring the pulling of hydraulic forces.
2: As in claim 1 rectangular members drilled and threaded to conduct
lubricants and to conduct heating or coolant fluid from the exterior
of a main base wall to within specific chambers under said base
plate of claim 1.
3: As in claim 2 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 base plate of claim 1.
4: 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 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.
5: In a crusher of the gyrating cone type an upright member having
a conical bearing quality surface above a cylindrical section joined
to a flanged section; said flanged section having multiple bolting
holes and a flat bottom face; said upright member has a hollow interior
and a pocket for a gear and means to prevent mixing of oil with
a heating/cooling fluid.
6: As in claims 4 and 5 a conical upright member drilled to connect
to multiple spaced apart grooves machined or cast into a conical
zone beginning a designed distance from the large end of the taper
to a designed distance short of an annular groove machined 90.degree.
to the axis of said member. An upper conical zone having multiple
similar grooves beginning a designed distance from a second annular
groove and terminating a designed distance short of the upper end
said tapered upright member. Drilled oil holes from base surface
of said conical member to crossholes from said grooves to intersect
holes from base surface to cross-holes.
7: As in claims, 5 and 6 an upright conical member having a bearing
quality cylindrical extension above said conical upper conical zone.
Said extension having means of lubrication. One or more holes drilled
from base of upright member to connect to cross-holes from root
diameters of said two annular grooves.
8: As in claims 4 5 and 6 an upright conical member having multiple
oil holes positioned to supply oil pressured to supply hydrostatic
lift and lubrication to lower and upper zones on the conical surfaces
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.
9: In a crusher of the gyrating cone type an upright conical member
bolted to a base plate; oil ways drilled to supply oil to multiple
vertical grooves on its exterior taper, and to two annular grooves
between a lower zone and an upper zone and to a cylindrical extension.
above said upper zone.
10: As in claim 9 an upright conical member drilled through to
conduct oil to a thrust bearing bolted to top of said member. Tubular
connectors with sealing rings close fit to matching holes in top
of conical member and bottom of thrust bearing. Said connectors
conduct oil across a space between conical member and thrust bearing.
11: In a crusher of the gyrating cone type an upright conical member
attached to a base plate at its largest diameter; a thrust bearing
attached with a forced fit to the top of said upright member and
shimming means for vertical adjustment; cap screws retaining said
thrust bearing and passing through said shims to prevent said shims
from moving; said shims insertable and removable with thrust bearing
in place. 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.
12: In a crusher of the gyrating cone type an upright conical member
having a lower flange drilled for insertion of multiple closely
space socket head cap screws, interference fits at its outside diameter
and its inside diameter with a supporting member machined to accept
said conical member. Said support member drilled and threaded to
receive said cap screws. Several threaded holes in said flange for
jacking screws to extract said tapered member from its interference
fit.
13: In a crusher of the gyrating cone type an upright conical member
having an exterior taper of large enough angle to prevent radial
clamping of another over laying member. A conical surface having
a very smooth bearing quality finish, and upper and lower zones
separated by one or more annular grooves; said zones each having
several evenly spaced grooves each in approximately the same plane
as the axis of the conical member, passageways from its base surface
to join with intercepting passageways from said grooves, lubricant
to flow from base to grooves all separate and individual. Within
said conical member a hollow chamber for containing a cooling/heating
fluid flowing in and out of said chamber. A concentric tubular member
of a specific diameter extends downward into said chamber a designed
distance, and an end cap welded liquid tight to said tubular member;
the top end of said conical member machined to fit the outer diameter
of said tubular member and welded liquid tight to said tubular member.
14: In a crusher of the cone type having an upright conical member,
the top end having a machined inside diameter to accept the outside
diameter of downward projecting cylindrical section of the body
of a thrust bearing member with a slight interference fit, and threaded
holes to receive cap screws; the top face of said conical member
is 90.degree. to the axis of said member through 360.degree.; said
thrust bearing member having said slight interference fit; its top
face is drilled and countersunk to receive cap screws through the
thrust bearing body and into said threaded holes in said conical
member thereby holding said thrust bearing firmly. Said thrust bearing
having threaded holes for extracting screws.
15: As in claim 14 an upright conical member having its top face
machined to have threaded holes and between said holes smooth bored
holes to receive tubular connectors to transfer pressurized lubricant
between said conical member and a thrust bearing member, and said
tubular connectors having sealing means to prevent the escape of
lubricant.
16: In a crusher of the gyrating cone type a lower part of a thrust
bearing having an attachment to an upright conical member for support;
a steel body 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 steel
concave 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 having an opening through
its axial center of a designed diameter.
17: In a crusher of gyrating cone type an upstanding conical member
concentric to the centerline of a main frame and firmly attached
to a base plate centered on crossbeams of said main frame. A rotatable
member having the same inside taper as said upright conical member
and the same large end diameter or slightly less diameter for wear
compensation, and a cylindrical extension above the small end of
said inside taper having its inside diameter concentric to said
upstanding conical member, and between said inside taper and said
conical extension an annular groove with drain holes through the
wall of said extension. Said rotatable member has an outer conical
taper that is larger in included angle than its interior taper;
the centerline of the outer angle is offset and canted to the mainframe
axis but intersects said mainframe axis at a designed distance above
said rotatable member thereby establishing a vertex. A cylindrical
extension above the small end of outer cone has arcs of varying
degrees and radii with each centered on the outer angle. The offset
creates a varying amplitude of gyration that is proportional to
its distance from said vertex as said rotatable member is gyrated.
18: As in claim 17 a rotatable eccentric member having an inside
conical bore open at both ends, an outside conical surface with
its conical vertex above the vertex of said inside conical bore,
vertices on the same centerline but forming an angle between their
centerlines, holes joining the two conical surfaces, the inner ends
of said holes aligned to annular grooves in an upright conical member,
the outer ends of said holes entering grooves cut in outer conical
surface, and nozzles threaded into said outer ends, and one or more
grooves open at both ends to relieve hydraulic pressures in a chamber
above said eccentric member.
19: As in claim 17 a rotatable one piece eccentric member without
bushings normally composed of cast bronze but could be of other
suitable material e.g. aluminum. The bottom face of said eccentric
member is drilled and threaded for cap screws and keywayed for drive
keys for attaching to a driving member. Said eccentric member having
a conical bore and a larger conical outer surface.
20: In a crusher of the gyrating cone type a rotating member of
designed thickness having one outer radius through 180.degree. or
less, tangential extending sides, a longer outer radius from one
tangential side to the other tangential side. A bored hole is concentric
to said two outer radii and to an upright conical member and has
a larger bore than the diameter of the lower cylindrical section
of a nonrotating upright conical member that it surrounds. The lower
face of said rotating member operates 90.degree. to its axis of
rotation. A portion of its upper face is recessed parallel to its
lower face and is attached and keyed to an eccentric member as in
claim 17; an outer recessed portion is canted 90.degree. to the
centerline of an eccentric member having a conical surface of bearing
quality which has an axis angular to the axis of rotation. Said
canted surface is machined to retain a sealing ring and an annular
recess for operating clearance of a gyrating eccentrically canted
member and for draining lubricating oil and holes for draining said
oil. The remaining top surface of said rotating member is parallel
to the lower face.
21: As in claim 20 a rotating member attached to an eccentric
member and having an extended diameter and thickness to serve as
a counterbalance and support and attachment for 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.
22: As in claim 21 a rotating member having means to attach fine
tuning counterweights to the underside of said member and to do
so without being hindered by any other members of the machine.
23: A rotatable member having an outer radius of 180.degree. or
less and two tangential edges terminating at a longer outer radius
and a portion of the top face canted to the bottom face and includes
holes and keys to hold and drive an eccentric member rotatably.
Said longer radius extension is parallel to said bottom face and
has a midpoint 180.degree. to an eccentric offset. Said extension
acts as a partial counterweight and a platform with means for attaching
more counterweights to balance gyrating forces. The underside of
said rotatable member is formed to receive and retain an internal
tooth gear and a sealing ring. The portion of canted and offset
top face is also machined to receive a sealing ring. Drain holes
are drilled to convey lubricant through said rotatable member.
24: In a crusher of the gyrating cone type a segmented shielding
means supported on cross beam means to surround and protect a rotating
member or members from impacting material after said material has
exited the crushing chamber. Said segmented shielding means may
be installed or removed without obstruction by other members.
25: In a crusher of the gyrating cone type a gyrating member having
a converging conical internal bearing surface for radial loading,
a cylindrical internal surface above the conical surface, Said cylindrical
surface terminating at designed length with a short taper to a larger
cylindrical surface of a designed length that terminates against
a flat surface. A cylindrical recess smaller in diameter than the
cylinderical diameter that is between the first and second conical
surfaces, a flat surface at the termination of said cylindrical
recess, and said flat surface having threaded holes to receive fasteners;
at the inside diameter of said flat surface is a short conical taper
to a smaller cylindrical smooth surface extending axially a designed
distance and terminating at a conical surface that contains holes
parallel to the axis of said gyrating member; last said conical
surface terminates at a smaller cylindrical bore that extends through
the top of said member. In this bore is machined an annular groove
of designed dimensions to retain an elastomer sealing ring. At the
top exit is a flat surface. At the periphery of said flat surface
is the top of a frustrum of a conical surface that diverges outward
at a large included angle to a diameter terminating at an annular
flat surface; a second conical surface extends from said flat surface
to the largest diameter of said gyrating member at which a cylindrical
section extends downward a designed distance terminating at a flat
surface; at the inner diameter of said flat surface are alternating
but evenly spaced struts and hollows joining the wall of the larger
outer conical section to a smaller conical wall formed between said
smaller wall and said bearing conical section; a diverging conical
section extends outward to a narrow cylinderical diameter; a sealing
ring retaining means is machined at said cylindrical diameter; a
flat surface extends inward some distance to a second cylindrical
surface that terminates a designed distance below said converging
conical internal bearing surface.
26: As in claim 25 a gyrating conical member having a replacible
wear member over-laying and matching the contour of said gyrating
member on its outer conical seating area; inward conical surfaces
are spaced for backing material; said wear member has a concentric
conical recess to the axis of said gyrating member and of designed
diameter; a conical spacer seats in said recess; a large cap screw
with a double conical head seats into said spacer, and its threaded
portion engages female threads in an extended cylindrical member;
said cylinderical member is taper threaded into a piston member
having a conical upper surface that has two or more close fitting
pins projecting vertically from said conical surface and parallel
to the axis of said gyrating member; said pins engage clearance
holes in said gyrating member; a sealing means between piston diameter
and a matching cylindrical bore in said gyrating member; a sealing
means between said extended cylindrical member and smallest bore
in said gyrating member; a valving mechanism in the bottom face
of the threaded bore of said extended cylinderical member; a hole
from the top tapered thread to valve hole in said cylindrical member;
a means for injecting hydraulic fluid into and through said valving
mechanism and into a cavity formed between said two sealing means;
a threaded hole in said double conical head cap screw; a means to
release said hydraulic fluid; a protecting wear cap retained over
said cap screw. The wearing face of said replacible wear member
may be of any desired contour.
27: In a crusher of the gyrating cone type 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; said disk is centered in a matching recess of the
member of claim 25 and is retained by cap screws; said disk having
a center recess to contain a universal joint; one part of said joint
is attached to the bottom face of said recess by cap screws, and
its other part having one half of a jaw clutch attached to it; said
jaw clutch having means to 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 coil spring surrounds the assembly of joined
splines and is partially compressed at assembly; a retaining means
prevents the spring from disengaging said splines. Said spherical
surface case harden and super finished
28: As in claim 27a 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 as in claim 14; its
bottom end is flanged inward and bored to match the boss of said
hydraulic motor and is drilled and threaded for attaching said motor
by cap screws and locking nuts. A universal joint as in claim 27
is coupled to said hydraulic motor.
29: As in claims 27 and 28 a pair of universal joints with a jaw
clutch and a coil spring between, the upper universal joint coupled
to an eccentric gyrating member, and the lower universal joint coupled
to a hydraulic motor on centerline of a main frame to convert eccentric
orbiting torque to concentric torque. A means to align and couple
both halves of said jaw clutch for inaccessible blind assembling.
30: As in claims 27 and 28 a hydraulic motor coupled through a
drive assembly of universal joints and a jaw clutch to restrain
a gyrating member from turning with an eccentric driving mechanism
when running freely, but does not resist retrograde rotation of
said gyrating member when crushing rock or other crushable material.
31: As in claim 31 a hydraulic motor restrained against rotation
in one direction but is not restrained in the opposite rotation
by a valving mechanism having an intake valve that opens to allow
oil to pass freely through the motor and out a discharge port without
restrictions; however, when attempts to turn in the opposite rotation
are imposed on the motor the intake valve closes, and oil is forced
against a spring loaded valve that has an adjustment for varying
resistance to said force; it is desirable to adjust spring force
to hold against normal frictional torque but to open if torque from
harmful causes occur.
32: As in claim 29 an assembly of universal joints, an automatic
coupling of male and female halves of a jaw clutch, a splined slip
connecting member, a coil spring urging splines apart, a means to
prevent splines from separating, and all enclosed in a chamber that
prevents the mixing of lubricant with heating/cooling fluids.
33: In a crusher of the gyrating cone type a safety relief system
having accumulators connected in parallel to manifolds consisting
of tubular members free to turn within header plates containing
sealing means, and sealing means between said header plates and
anchor plates as in claim 1 vertical tubular members from slip
connectors joined 90.degree. to said manifolds to 90.degree. slip
connectors fused to cylinder walls; said slip connectors have a
close fit to tubular members at their entry but having diverging
internal conical shapes starting at sealing means of said slip connectors,
thrust supporting means for manifolds directly under slip connectors;
cylinder members connected to anchor means by link and pin means;
rods joined to piston means within cylinders extend through cylinder
header means and have taper threaded means to couple tightly with
clevises; hook like members pinned to devises and overlap a flange
on a bowl nut means; self aligning disk means located between hook
like members and said flange; lower halves of self aligning means
are of nonferrous metal of convex form on one side and flat on the
other side and are held in position by an integral extensions into
holes in said flange or recessed to receive pin alignment; upper
halves of self aligning means have concave shapes matching said
lower halves and are grooved on top faces to width of hook like
members to insure exact centering alignment of said hook like members
prior to welding. A greasing means in upper halves.
35: As in claim 33 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
an manifolds are not made to tilt.
36: In a crusher of the gyrating cone type a shaftless gyrating
member having an axis eccentric angled to a main axis; a convex
half of a hydrostatic thrust bearing centered to the eccentric axis
and having an axial positioned recess and a universal joint attached
within said recess; said universal joint having one half of a jaw
clutch coupled to said joint, said clutch having a male conical
extension to enable blind coupling with the other half of said jaw
clutch which has a female conical shape to guide a male conical
extension to couple jaws of said clutch; a concave half of a hydrostatic
thrust bearing is centered on the main axis and mounted on top of
an upright conical member that is bolted to a base member; said
concave thrust bearing has a center opening large enough to accommodate
a gyrating universal joint and jaw clutch; said clutch has a splined
drive shaft to a second universal joint coupled to the shaft extension
of a hydraulic motor. A coil spring to force both halves of jaw
clutch to firmly couple; means to prevent said splines from uncoupling.
The body of said motor is attached to a depending tubular member
having a top flange bolted to a conical taper upright member. Said
motor and attached tubular member is suspended within a larger tubular
member built into said conical upright member. The body of said
motor is restrained from rotating in either direction. A valving
body that permits motor shaft to turn freely in one direction but
retards in the opposite direction by a one way check valve that
allows fluid to enter but not to escape. Hydraulic fluid is free
to pass through when the motor turns in one direction but is restrained
in the opposite direction by a second valve that is spring loaded
but will allow fluid to pass when pressure overrides spring pressure;
a means of adjusting pressure resistance, and unrestricted entry
of fluid to motor in either direction of rotation.
36: As in claim 35 a valving body having an intake valve that
allows free intake of fluid and to pass said fluid through its body
but closes if fluid reverses flow; reverse flow is permitted if
excessive pressures occur to override a spring loaded adjustable
check valve. Said valve body configured to be attached to a hydraulic
motor that is confined within a close fitting tubular housing.
37: As in claim 35 a hydraulic motor suspended within a tubular
member configured to prevent mixing of lube oil and a heating/cooling
fluid, suspending member vented to allow enclosing member to fill
with lubricant and a vent in the enclosed chamber to relieve hydraulic
pressures.
38: In a crusher of the gyrating cone type, a means of adjusting
the space between the fixed wear member and the gyrating wear member
to control product sizes and to separate a rotatable member from
a fixed member, said means 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.
39: As in claim 38 a means to clamp a rotatable member from turning
within a fixed 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.
40: As claim 38 a means to power rotate a rotatable member; said
means having an enclosing housing having an arcuated inner wall
centered off the main axis of a 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 said
enclosed housing is a slidable member that extends through openings
in uppermost end spacing members, roller assemblies near each opening,
a push-pull hydraulic means pin connected to said slidable member
and to a spacing member, said slidable member angled to same as
thread angle; a swing pawl journalled to the inside face of said
sliding member and having vertical bars at end of pawl and parallel
to said axis; said bars spaced to straddle multiple evenly spaced
vertical lug bars on a 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 covers to protect
said extensions. A cover member encloses the top of said housing.
41: As in claim 38 two hydraulic powered members bolted to platforms
integral to a fixed 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 second
rotatable member that is threaded into said fixed threaded member;
said pawls are powered to engage and disengage gripping said lug
bars; means to accommodate hydraulic oil captured between the pawls
hydraulic cylinders and a control valve as pawls are forced radially
throughout their arc of travel. Said powered members enclose their
working members.
42: In a crusher of the cone type a rotatable bowl member having
an internal conical chamber designed to receive and retain replacible
wear liners; both bowl and liners have matching conical seating
contact at the outer diameters of said liners; both bowl and liners
have converging conical spaced apart surfaces that terminate at
designed diameters; said liners have a near cylinderical vertical
extensions terminating at a diverging conical flange of a designed
cylinderical diameter of designed thickness; said seating contacts
are machined surfaces as are diverging conical flanges, cylinderical
diameters and top surfaces of said bowl liners; said bowl has an
inside diameter slightly larger than said cylinderical diameters
of bowl liners to enable bowl liners to pass their conical flanges
through bowl's inside diameter. Slidable members having wedging
ramps to match liners' conical flange and having elongated bolting
slots and having outer ends with vertical extensions with slots
to lock bolt heads from turning and bolts with nuts and washers
bearing against fixed thrust members; washer plates covering said
elongated slots and cap screws through said washers and slidable
members; guides at each side of slidable wedges prevent skewing
of said wedges.
43: In a gyrating crusher of the cone type an assembly of parts
and members all interdependent to make a functionally operating
machine: 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 other beam in two sections abutting
first 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 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 in a tight recess in said support member
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 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
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; a 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. Resting upon said thrust
bearing and journalled on said conical eccentric member is said
gyrating conical member having a replacible 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 V-ring inserted into its
top flange and upon said V-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 means;
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 joins 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 V-ring member with self aligning means between
said flange and said hook like means; accumulator means connected
in series with said manifold means 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 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; a locking means has 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 under face of the top flange of said flanged member; means thereby
locking and unlocking said rotatable member. Said rotatable member
contains a replacible 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 flanged threaded member relative to main frame
member by downward projecting means attached to flanged member bearing
against blocking means attached to top flange of said main frame.
Description BACKGROUND OF THE INVENTION
[0001] 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
[0002] 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
[0003] Having introduced the purpose of this application, we now
list the numbers that we have assigned to its parts. We refer to
drawing pages 1 through 22 and FIGS. 1 through 49. The purpose each
part serves will be explained later.
[0004] Page 1 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; 400 is a driven
sheave.
[0005] Page 2 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.
[0006] Page 3 FIG. 3 is a vertical section view through the crusher;
33 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.
[0007] Page 4 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;
[0008] FIG. 5 is a vertical sectioned view through B-B' FIG. 4;
35 are oil drain ports in beams.
[0009] Page 5 FIG. 6 is a vertical sectioned view taken through
C-C' of member 10
[0010] 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 21 30 is a gear inspection hole, 14 is an oil deflector, 33
and 34 are larger oil holes than 17 25 and 26 are heating/cooling
fluid holes, 27 is an annular oil drain;
[0011] 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.
[0012] FIG. 9 is a detailed view of 13 and 27 taken through F-F'
FIG. 7;
[0013] FIG. 10 is a detailed view taken through D-D' of FIG. 7
showing deflector 14 and nozzle 15; 142 is an oil hole.
[0014] Page 6 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;
[0015] FIG. 12 is a vertical view of 38; D is a large diameter
of taper 43 and D' is its small diameter; 48 is a cylindrical extension
of D' diameter; 49 are hydrostatic lubrication grooves; 39; are
annular grooved lube oil distributors.
[0016] FIG. 13 is a detail of grooves 39 and 55 oil lines;
[0017] FIG. 14 details transfer nipples 50 with one of two elastomer
seal rings 51 in place.
[0018] Page 7 FIG. 15 is a plan view of the bottom face of spindle
38; 41 are multiple lube oil holes; 52 are multiple lube oil holes;
55 are oil holes; 53 is a fluid inlet; 54 is a fluid outlet;
[0019] 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;
[0020] FIG. 17 is an enlarged view of annular grooves 39
[0021] Page 8 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,
[0022] 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;
[0023] FIG. 20 is an enlarged view of 68;
[0024] FIG. 21 is an enlarged view of nozzles 69.
[0025] Page 9 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 pressure relief 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;
[0026] 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.
[0027] Page 10 because of an over-sight Page 10 was drawn after
all other FIG drawings were established and numbered, consequently
its FIG numbers are not in sequence as they should have been; however,
page numbers are in sequence for a better understanding of how parts
fit together. FIG. 48 is a plan view of the eccentric drive plate
150; E is the eccentric offset and the center of radial line R-1;
R-2 R-3 and R-4 are centered on the machine's center line; E/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; 72 are threaded
holes; 80 are dust seal retaining bosses; FIG. 49 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.
[0028] Page 11 FIG. 24 is a vertical view of 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);
[0029] FIG. 25 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.
[0030] FIG. 26 is a sectioned plan view of 75 and 76.
[0031] Page 12 FIG. 27 is a vertical section view of cone head
75; 100 is the vertex of center lines 101 and 102 103 is the amplitude
of gyration; 78 are multiple struts, 79 are cavities; 81 is a converging
conical bearing surface; 82 is a cylindrical bearing surface; 89
is gyrating clearance; 92 is a conical surface; 88 is a smooth precision
bore; 85 is a conical surface; 80 is a positive angled boss; 90
is an annular seal ring groove; 91 is an extended cylindrical section.
[0032] Page 13 FIG. 28 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.
[0033] FIG. 29 is an enlarge sectional view of 110; 11 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 fitting.
[0034] Page 14 FIG. 30 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; 193 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 lock 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.
[0035] Page 15 FIG. 31 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 clamping 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 hole
in 160.
[0036] FIG. 32 is a cut away view of 168; 180 is a valve seat;
181 is a ball; 179 arc 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.
[0037] Page 16 FIG. 33 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 T fittings; 199 are
lube oil tubes from Ts 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
than 204 and 205; 208 and 209 are heating/cooling fluid connectors;
292 293 and 295 are detailed on page 19 FIG. 40.
[0038] Page 17 FIG. 34 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 V-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;
[0039] FIG. 36 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. 35 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. 250 is a slidable member; 253 is; 265 is a
bowl wear liner; 262 is an elastomer dust seal.
[0040] Page 18 FIG. 37 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 retaining 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;
[0041] FIG. 38 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.
[0042] Page 19 FIG. 39 is a tangential 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 are cylinder assemblies;
D is cylinder diameter; S is ram diameter; 280 are devises; .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; R is a long radius centered at lowest
277 pin ; r is a shorter radius centered at clevis pin.
[0043] FIG. 40 is a radial view of FIG. 39; 287 is a lubrication
fitting; 293 is a tube manifold with slip connector 292 joined to
it; 297 are saddle blocks; 298 are thrust transfer members; 296
is a threaded hole into one 294; 289 is a 90 deg. attachment to
275; 290 is a connecting tube of d diameter; 300 is an air bleed
valve; 301 is a spacing pad; see FIGS. 41 and 42 page 20 for detail
of 275.
[0044] Page 20 FIG. 41: 306 is a 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 S diameter; D is cylinder diameter;
D' is a diameter larger than D; 318 is a travel space; 317 is an
elastomer seal; 323 is a taper in 292 and 289; L is the distance
from the center line of 275 to the center line of 290; N is an offset;
324 is an eye plate welded to 275;
[0045] FIG. 42: 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.
[0046] Page 21 FIG. 43 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; 361 362 376 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.
[0047] FIG. 44 is a plan view of FIG. 43; 242 and 244 are a section
of the adjustment ring 243; 370 is a bi-directional 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;
[0048] Page 22 FIG. 45 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.
[0049] FIG. 46 is a plan view of FIG. 45; end spacer plate 382
is cut out for bar 364 at both ends; plates 390 FIG. 47 fill openings
above 382.
[0050] FIG. 47 is an end view of 326 adjusting assembly; 390s are
attached to cover 381; 391 are clamps to hold 380.
[0051] 18 is for all drains not otherwise numbered and is used
in several different FIGS.
DETAILED DESCRIPTION OF DESIGN OF PREFERRED EMBODIMENTS
[0052] Page 1 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. Both accumulators
are connected to manifold tubes 293; vertical tubes 290 conduct
pressurized oil from 293 to hydraulic cylinders 275. Hook shaped
members 281 are connected to hydraulic cylinders 275. Column 298
transfers the thrust of 290 into the main frame l-MF, because 290
has slip connections at each of its ends and therefore acts like
a piston. 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 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 liners, replace
with new, pour backing epoxy, and reassemble within three hours
in the more popular mid size crushers; no other cone crusher can
closely match this. When down time of such costly operations as
rock plants are is factored in, the cost savings of our design are
enormous! 24 is a lube oil drain to a reservoir not shown; 224 is
a stop block that resists the torque of depending arm 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 antirotation stops;
usually there is wear between antirotation 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 lift of 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. 318623
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; 400 is a driven V belt
sheave that transfers power input to activate all rotating and gyrating
members.
[0053] Page 2 FIG. 2 shows the main frame with bowl assembly removed;
hooks 281 and cylinders 275 are tilted outward to their stop position
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.
[0054] Page 3 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 insure
constantly the exact spacing of bearings 131 and to prevent any
erosion of bearing housing 156; 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. 28 page
13 details said concepts.
[0055] Page 4 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 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 center 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 the upper faces of members 4
5 and 6 are face machined simultaneously with beams 2 with all
in the same plane; the radius and lower ends of members 3 are machined
concentric to the Frame's axis and to the same radius as the inside
diameter of wall 1-W; 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 page 5 FIG. 7 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; 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 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 premachined at its inside and outside diameters and one face;
the inner bore has a small chamfer, and 1-W has a hand ground chamfer
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 39 page 19
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.
[0056] Page 5 FIGS. 6 and 7 detail member 10's construction before
welding to beams 2 and chambers formed by 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 a spindle; multiple
holes 19 are precision drilled and partially 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 gear meshing; holes 17 with recesses 16 FIG. 8 are precisely
positioned as are holes, 33 34 25 and 26 to match holes in said
spindle; gear inspection hole 30 is drilled; annular groove 27 and
a boss for positioning member 13 are machined; multiple drain holes
18 are positioned to avoid being obstructed by beams 2; hole 12-H
is drilled on center; 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.
[0057] Page 6 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 hubs 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. The conical construction
of our new concept design has an area at D dimension and a smaller
area at D'; a cylindrical extension 48 of D' diameter stabilizes
an eccentric member 65 FIG. 18 page 8 when the hydrostatic oil film
is too thick; the area difference of D minus D' is substantial enough
to provide an adequate hydrostatic thrust bearing when lube oil
under pressure is ejected 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 which causes reverse end loading
of the gear teeth during every 360.degree. of rotation. Also constant
shrinking and expanding of such bushings causes myriads of tiny
cracks resembling a dried mud flat; the oil film is disrupted adversely
affecting lubrication. Our design 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, and original and maintenance costs are substantially
less with our design. However, our hydrostatic bearings are not
without fault; when operating unloaded a surplus of oil and varying
viscosities can cause too thick an oil film which creates instability;
the short cylinderical section, 48 FIG. 12 at the top portion of
the spindle stabilizes the eccentric. FIG. 11' is a plan view of
the top of said spindle; 40 is a bolting flange; 41 are multiple
countersunk holes for large cap screws; 43 is a conical super accurate
smooth surface; 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. 31 Page 15; 49 are spaced apart
annular grooves around extension 48 to supply hydrostatic lubrication
between 48 and eccentric member 65;44 are smooth wall holes for
tubes 50; 45 are threaded holes for retaining said thrust bearing;
47 is a chamber enclosing a spur gear. Surfaces 43 and 48 are machined
to near zero tolerances and extremely smooth finishes; the fluting
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.
Hydrostatic lubrication to a thrust bearing positioned on top of
said spindle is held in place by a slight press fit in bore 59 and
by cap screws threaded into holes 45; tubes 50 sealed by O-rings
51 transfer lube oil across the space between the spindle and thrust
bearing; gun drilled holes from the base of 38 to holes 44 transfer
oil to tubes 50.
[0058] Page 7 FIG. 16 shows a vertically sectioned view of said
spindle; 61 is an as cast hollow chamber with a 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 keep lube oil at the
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 cold weather. 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 page 15 FIG. 31; 56 is a precision bored recess
to hold thrust bearing 160 in radial position; 58 is a solid cover
with a sealing ring 59 and is retained in place by ring 60 that
engages a groove; its purpose is to prevent heating/cooling fluid
from mixing with lube oil; oil lines and h/c 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
water with antifreeze; 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 deliver lube oil to annular grooves 39 that continually supply
lube oil to holes 68 through eccentric member 65 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 heating/
coolant fluid to chamber 61 in said spindle, and 62 withdraws it
near the top of said chamber.
[0059] Page 8 FIGS. 18 and 19 and page 9 FIGS. 22 and 23 show the
eccentric member 65 which is a non-ferrous bearing quality one piece
casting; the taper of inner conical surface 73 is an exact match
to the taper of spindle member 38; step bore 74 registers on a matching
boss as shown in a partially assembled view on page 10 FIG. 49.
Because it is not possible to use flow dividers to control oil flow
to the outer bearing surface, we use nozzles 69 and vary the hole
sizes to force the oil volume as best served; 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 page 12 FIG. 27; open ended valleys 67 drain
lube oil to prevent pressure build-up in the space above the eccentric;
the eccentric does not contain bushings; it is a one piece member
and has four bearing surfaces, two conical and two cylindrical;
extension 48 has arc A-1 of less than 180 and a smaller arc A-2
that have just enough clearance for oil film; 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 thermal expansion by
bulging radially enough to eliminated clamping; 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. 24 are held concentric to their centerlines as is
a spherical thrust bearing 106 to said spindle. FIG. 28 page 13
and 160 FIG. 31 page 15
[0060] Page 9 FIGS. 22 and 23 keyways 70 and keys 77 page 10
FIG. 49 transfer driving torque and accommodate thermal expansion
and contraction without distorting eccentric member 65; cap screws
holding 65 to an eccentric drive plate 150 page 10 FIGS. 48 and
49 have sufficient clearances in holes 192 to accommodate thermal
movements of said eccentric 74 centers eccentric 65 on its drive
plate 150. 73 is the inner conical surface that rotates about spindle
member 38 and 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 which in turn discharge said oil just ahead of
arcs A-1 and A-2 for additional lubrication thereby preventing eccentric
65 from acting like a piston.
[0061] Page 10 FIGS. 48 and 49 as explained in Brief Description
of The Drawings, these FIG numbers are not in the best sequence.
Eccentric drive plate 150 is attached to said eccentric 65 by cap
screws on holes drilled on R-5 radius and is driven by keys 77;
radii R-2 R-3 and R-4 are centered on the main centerline of the
crusher; R-1 is a varying radius from centerline 102 that reaches
its maximum at the contact plane between eccentric 65 and eccentric
drive plate 150 130 is 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; 18 are
oil drains that flow lube oil back to a reservoir. The combined
weights of the cone head and mantle, 119 FIG. 24 page 11 establish
a c.g. that when gyrating eccentrically creates centripetal forces
that must be neutralized by counterweighting; the extended R-4 radius
provides about half the required counterbalance, and extra weight
required is provided by weights 51 FIG. 3 and fine tuned by weights
152 (see page 14 FIG. 30) that can be changed without removing the
cone head; an air space 153 is provided between each counterweight
plate by washers 154 so crusher dust can be ejected and minimize
any build-up of dust against the inside radii of said plates. 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
page 3 FIG. 3 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 a cooling effect to it. 80 is a positive angled boss to
retain seal 36 by shrink fit
[0062] Page 11 FIGS. 24 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 to said cone head (see page 13 FIG. 28) 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 backing that
hardens in a short time; 80 is a boss for retaining a sealing ring;
FIG. 25 is a plan view of the bottom: 78 are struts that transfer
crushing forces into the conical wall of bearing surface 81 FIG.
27; 79 are spaces between said struts to reduce weight; 84 are threaded
holes to retain a conical thrust bearing; 86 are two or more holes
evenly spaced ,we prefer using three, that lock a piston from rotating;
87 is a precision bore that serves as a cylinder; FIG. 26 is a segmented
plan view of the top.
[0063] Page 12 FIG. 27 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; 89
provides gyrating space around thrust bearing 160; 83 is a precision
recess to retain 106 the convex half of thrust bearing 160 page,
13 FIG. 28; 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; 90 is a seal ring groove and 87 is
a smooth bore for a piston extension to slide.
[0064] Page 13 FIG. 28 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 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 to pull
piston to face to face contact of its angled surface. FIG. 29 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. During crushing the
mantles on every kind of gyrating cone crushers tend expand due
to pressures of crushing; this phenomenon causes the mantle to creep
relative its cone head in the direction the cone head gyrates; washer
98 and cap screw 99 are constructed to turn with the mantle to insure
that the mantle stays tight against the surface 76; this results
in the cap screw or nut, whichever is used, becoming so tight that
it is impossible to unscrew; 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 because manganese steel cannot
be cut with gas torches; these are time consuming and costly methods
that 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 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 released 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 is fool proof,
and should the hydraulic oil escape from its containment the cap
screw will draw the piston tightly against surface 85 like other
cone crushers; 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. 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 rock dust must be removed first. Other members of FIG. 28 are
thrust bearing 106 having a spherical radius centered at vertex
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.
[0065] Page 14 FIG. 30 shows vertical sectioned layout of our double
reduction gear train; 125 is the power 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 to deliver lube oil to outer bearing 131 in combination with
dike 145; 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 made integral; 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 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; 18 is an oil drain; 35 are drain port in beams 2; this system
insures obtaining and maintaining proper bevel gear meshing; spur
gear 129 does not require meshing adjustment. Internal tooth gear
130 is attached to eccentric drive plate 150 which in turn is attached
to eccentric 65 as previously shown in FIG. 49; 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. FIG. 30 shows labyrinth seals 36 seal spacer
37 counterweights 151 air spaces 153 spacers 154 and fine tuning
balancing weights 152. An 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 maximum strength
with a substantial reduction in weight and costs.
[0066] Page 15 FIG. 22 is detailed vertical sectioned view of the
thrust bearing 160 and cone head braking mechanism; 161 is an 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 annular grooves spaced apart by closed ends; tubes 50 with sealing
rings 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 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
is free to turn in one direction but resist turning in the opposite;
an enlarge view FIG. 32 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 the motor
is forced to turn opposite, ball valve 181 closes, and oil is then
drawn in through port 189 and to escape must force ball valve 186
to open which compresses spring 187; by-pass 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, 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 h/c 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.
[0067] Page 16 FIG. 33 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 page 19.
[0068] Page 17 FIGS. 34 & 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; 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 252; 258 are guides to prevent skewing of wedges;
266 is a wedging ramp with a conical radius to match liner's; 120
is backing material usually epoxy but could be zinc which are poured
in their liquid state but soon turn to solids. Not shown are pouring
spouts built in to save workmen from making them every time new
liners are installed. 248 is a hopper to keep rock away from damaging
wedging system members. A crusher must have a means of adjusting
for whatever size product maybe required and to compensate for wear
of liners; Most gyrating cone crushers use a threaded means to achieve
that; a problem with threads is potential galling between two similar
metals; to cope with this problem we provide a small groove on the
loaded face of the female thread 227 FIG. 35 in bowl nut 220 and
a means of injecting special greases either by hand pumps or automatic
lubricators through multiple places 228; the start and end of said
groove is blocked as well as intermittently between said 228s; a
lock nut 235 is restrained from turning by means of three equally
spaced pins, 330 FIG. 3 but can move vertical a short distance;
alter an adjustment is made, hydraulic fluid under pressure forces
multiple pistons 232 against thrust rods 234 which causes said lock
nut to lift bowl 240 and hold it firmly against thread flank 226;
said pressure is maintained between adjustments in hoses 270 one
of which is shown in FIG. 37 page 18; a P.O. check valve at the
control, not shown, retains the constant pressure between the pressure
source and cylinders 230. Adjustment ring 243 is bolted to the top
flange of bowl 220 and it has vertical lugs 244 evenly spaced around
its perimeter. Page 21 FIGS. 43 and 44 detail the power adjusting
system. V-ring 218 has a means of receiving injected grease to minimize
fretting between it and bowl nut 220. 263 is a replacible abrasion
resistant liner bolted to the inside of wall 1-W to protect said
wall from erosion of the crushed rock. 245 are bracing gussets with
openings 264; hydraulic hoses for the adjusting means are passed
through these openings.
[0069] Page 18 FIGS. 37 & 38 show in enlarged detail our bowl
nut locking system; a gap between band 268 and a shoulder on the
top flange of bowl nut 220 provides space for a dust excluder 236;
multiple cylinders 230 are clamped to the underside of said flange
by cap screws 231 that are sized to cope with whatever pressures
are imposed on pistons 232; high pressure seals 237 retain pressurized
oil, but if any leakage develops each cylinder is easily removed,
seals replaced, and cylinders re-attached; rectangular cylinder
bodies are through drilled and threaded 271 to receive connector
fittings, and all are connected in series by lines 233 either tubing
or hoses; small holes from cylinder heads to holes 271 feed oil
in or out of said cylinders; two hoses 270 approximately 180 deg.
apart conduct hydraulic oil to and from all cylinders for balanced
oil flow between a T connector and one hose to a P.O. check valve.
[0070] Page 19 FIGS. 39 & 40 and Page 20 FIGS. 41 & 42
combined show our new concept relief system; FIG. 39 is a tangental
view of one of several assemblies; 294 is an anchor plate that resists
the pulling force of cylinder 275; links 276 and pins 277 couple
said cylinder to 294; 278 are retaining rings to keep pins 277 in
place; 280 is a clevis joining piston rod 307 to hook like member
281; 282 is a concave disk centered on the line of tension and lightly
welded to 281 by welds 288; 282 centers on convex disk 283 that
has either a projection or a recess and pin that centers it on holes
284 all equal-distant from the center-line of the bowl nut 220 and
are usually equally spaced circumferentially; block 286 contains
a headless screw and rests on an inward projection of 281 and is
held in place by a small bolt; a spherical head shoulder pin 285
is secured in the lower end of hole 284; screws in 286 are adjusted
to barely touch 285; this system prevents hooks 281 from disengaging
pads 283 when the system is not pressurized. When the system is
pressurized, entrained air is bled out by valve 300 then each unit
pulls 220 downward onto V-ring 218 with great force. During normal
rock crushing tight contact is maintained between 220 and 218 but
should a non crushable object enter the crushing chamber the forces
generated will lift the bowl assembly and override the gas pressures
in the accumulators as oil flows from the cylinders 275 through
tubes 290 and 293 and into the accumulators; this compresses the
gas (Nitrogen) somewhat, but because of the large size accumulators
we use, pressure increases are not excessive. This system prevents
disastrous damage to the crusher. Louis Johnson, a co-applicant
to this patent application, was granted a U.S. Pat. No. 3118623
for a similar but less sophisticated system. As explained earlier
our new system allows the assembly to tilt outward on radius R or
just the hooks on radius r; to do this blocks 286 are removed; valve
299 is opened, and hydraulic hoses with quick couplings are uncoupled;
either a lever is placed under the projections supporting 286 and
281s are pried off of pads 283 or a special tool using hole 302
is used; all this takes less than ten minute |