Abstrict A conical crusher head of a gyratory cone crusher is supported
by a spider arm cradle. Radially disposed and circumferentially
evenly spaced spider arm type support members of the cradle extend
outwardly through an annular material discharge path in the lower
portion of the crusher and through the generally cylindrical frame
of the crusher. A gyratory drive mechanism is disposed annularly
about the material flow path region and is coupled to the head support
members to gyrate the head.
Claims What is claimed is:
1. A gyratory crusher comprising:
a crusher frame;
a concave disposed and supported against an upper end of the crusher
frame, the concave having an inner crushing surface sloping radially
outward in a downward direction, and having a central material feed
opening at an upper portion of the concave and a bottom opening
larger than the central material feed opening at a base of the concave;
a spider arm cradle disposed beneath the base of the concave, the
spider arm cradle having spider arms extending from generally a
vertical centerline through the crusher radially outward beyond
the base of the concave;
a crusher head of conical shape disposed on and totaly supported
by the spider arm cradle generally centrally within the concave,
the crusher head having a conical crushing surface extending adjacent
the crushing surface of the concave, the crusher head and the concave
being spaced from each other and forming a material crushing chamber
there between, the crushing chamber having an annular discharge
opening about a periphery of the crushing head;
a spider arm cradle drive disposed annularly about the lower crusher
frame portion, the spider arm cradle drive engaging each of the
spider arms and moving each spider arm in a rotational path about
an axis of rotation, the respective axes of rotation of the spider
arms intersecting in an apex of gyration of the crusher head.
2. The gyratory crusher according to claim 1 wherein the spider
arm cradle drive comprises a drive ring supported by the crusher
frame for annular rotational movement in a plane transverse to the
vertical centerline of the crusher, the drive ring having first
and second camming surfaces disposed to cyclically move each of
the spider arms simultaneously through a cyclic displacement range
of horizontal and vertical displacement vectors, which vertical
and horizontal displacement vectors have cyclic magnitude changes
relative to each other to generate said rotational path about the
axis of rotation.
3. The gyratory crusher according to claim 2 wherein one cycle
of displacement of the first and second camming surfaces corresponds
to one revolution of the drive ring.
4. The gyratory crusher according to claim 3 wherein the spider
arm cradle drive further comprises a drive sheave coupled to a power
source to rotate in a plane parallel to the plane of rotational
movement of the drive ring, and drive belts coupling the drive sheave
and the drive ring, such that the drive sheave drives the drive
ring.
5. The gyratory crusher according to claim 2 wherein the spider
arm cradle drive further comprises a drive sheave coupled to a power
source and mounted for rotation in a plane parallel to the plane
of rotational movement of the drive ring, and drive belts engaging
the drive sheave and the drive ring to couple the drive sheave to
rotatably drive the drive ring.
6. The gyratory crusher according to claim 2 wherein the first
and second camming surfaces are repetitively convoluted and a camming
convolution includes between two adjacent ones of the spider arms
one cycle of displacement of a respective spider arm plus that angular
portion of a cycle that corresponds to the angular peripheral spacing
between adjacent ones of the spider arms.
7. A gyratory crusher comprising:
a crusher frame;
a support structure disposed and urged against an upper end of
the crusher frame, the support structure having a plurality of peripherally
spaced thread lugs extending inward from the support structure in
a helical thread pattern having a predetermined pitch;
a concave having external threads of the same predetermined pitch
of the thread lugs, the threads being engaged by the thread lugs
to support the concave at a selected height within the support structure;
a crusher head disposed within a lower end of the crusher frame
and having upward directed crushing surfaces extending toward the
concave;
means for totaly supporting the crusher head vertically with respect
to the concave; and
means for driving the crusher head in a gyratory orbit with respect
to the concave.
8. The gyratory crusher according to claim 7 wherein the means
for supporting the crusher head with respect to the concave comprises
a spider arm cradle disposed in the lower end of the crusher frame,
the spider arm cradle comprising a plurality of spaced spider arms
extending radially outward from a central vertical axis through
the gyratory crusher, and the means for driving the crusher head
in a gyratory orbit with respect to the concave comprises eccentric
drive means for driving the spider arms in a circular eccentric
path about a gyratory motion axis, the respective gyratory motion
axes of each of the spider arms intersecting in a gyratory motion
apex.
9. The gyratory crusher according to claim 8 wherein the spider
arms are spaced at uniform angular intervals with respect to each
other and the eccentric drive means is disposed peripherally about
the crusher frame.
10. The gyratory crusher according to claim 9 wherein the eccentric
drive means comprises a drive ring disposed peripherally about the
crusher frame and supported with respect thereto, the drive ring
including an eccentric camming shape having horizontal and vertical
surface elements of eccentricity, and means for revolving the drive
ring about the crusher frame.
11. The gyratory crusher according to claim 10 wherein the means
for revolving the drive ring comprises a drive sheave supported
to rotate about an axis parallel to an axis of revolution of the
drive ring, and drive belts coupling the drive sheave and the drive
ring for joint surface motion.
12. A gyratory crusher of the type which crushes materials between
a concave and a gyrating crusher head, comprising:
a spider arm cradle disposed generally centrally within the gyratory
crusher, the spider arm cradle having a plurality of spider arms;
a crusher head totaly supported by the spider arm cradle, the spider
arms of the spider arm cradle extending outward from the periphery
of the crusher head through a material discharge region disposed
annularly about the crusher head, the spider arms having respective
spider arm ends disposed externally of and annularly about the material
discharge region; and
means, disposed externally about the material discharge region
and engaging each of the spider arm ends for revolving each of the
spider arm ends about respective axes of gyration intersecting at
an apex, to gyrate the crusher head about the apex of gyration.
13. The gyratory crusher according to claim 12 wherein the means
for revolving each of the spider arm ends comprises a plurality
of eccentric motion generator means, each coupled to one of the
spider arm ends, and each operating synchronously with the others
to gyrate the crusher head.
14. The gyratory crusher according to claim 12 wherein the means
for revolving each of the spider arm ends comprises a drive ring
disposed annularly about, and supported for rotation externally
of the material discharge region.
15. The gyratory crusher according to claim 14 wherein the drive
ring is an annular drive gear, and the means for revolving each
of the spider arm ends comprises a plurality of eccentric motion
generator means, each motion generator means coupled to one of the
spider arm ends and having an input gear coupled to the annular
drive gear, whereby the annular drive gear drives; each of the eccentric
motion generators synchronously to gyrate the crusher head.
16. The gyratory crusher according to claim 14 wherein the drive
ring comprises first and second camming surfaces engaging each of
the spider arm ends, the first and second camming surfaces having
horizontal and vertical displacement vectors of cyclic magnitude
changes to cyclically revolve each of the spider arm ends through
the respective axis of gyration.
17. The gyratory crusher according to claim 16 wherein one revolution
of the drive ring corresponds to a single cycle of horizontal and
vertical displacement of each of the spider arm ends.
18. The gyratory crusher according to claim 14 further comprising
an external drive means for rotating the drive ring.
19. The gyratory crusher according to claim 18 wherein the external
drive means comprises a drive sheave driven to rotate in a plane
parallel to a plane of rotation of the drive ring, and drive belts
coupling the drive sheave and the drive ring, such that the drive
sheave drives the drive ring.
Description BACKGROUND OF THE INVENTION
The invention relates generally to a gyratory or cone crusher and
more particularly to an arrangement for driving a gyratory crusher
head of a gyratory or cone crusher.
Gyratory crushers or cone crushers are characterized by cone-shaped
crushing heads which are supported to undergo gyratory motion. A
crusher head of a gyratory crusher is centered generally about a
vertical central axis through the crushers. The gyratory or gyrating
motion of the crusher head performs a material comminution action
on material as the material moves downward through a space between
the head and an inner surface of a concave or bowl-shaped stationary
member. The bowl-shaped member or concave is disposed in an inverted
position generally over the cone-shaped crushing head. The bowl-shaped
member is centered on the vertical central axis of the crusher and
has an upper opening through which materials, such as rock, ore,
coal or the like are fed into the space between the crushing head
and the stationary, bowl-shaped member. The action of the crusher
typically distributes the materials annularly about the crushing
head. The materials typically move by gravity through the annular
space between the inner wall of the stationary bowl member and the
outer, cone-like surface of the crushing head. The annular space
between the bowl member and the crushing head is also referred to
as the crushing chamber. The gyration of the crushing head causes
the space at any specific radial position of the crusher to cyclically
increase and decrease in size.
State of the art gyratory crushers are generally driven by a horizontally
disposed countershaft which radially extends into a lower part of
a generally cylindrical crusher housing. An inner end of the countershaft
is coupled through a pinion and ring gear to an eccentric bushing
or eccentric element to rotatably drive the eccentric element. The
eccentric element, in turn, is generally coupled to a connecting
shaft of the crusher head to bring about a desired gyratory motion.
A known, but generally accepted, disadvantage of the described
gyratory drive arrangement via the countershaft is that crushed
materials and the crusher drive share common space in the lower
part of the crusher housing. The crushed materials exit through
a lower end of the crusher housing, thereby all crushed materials
pass peripherally about the drive coupling to the crusher head.
Thus, crushed debris accumulates on protective covers of the drive
train. As long as no maintenance is required on the crusher, the
drive train position in the lower part of the crusher housing may
be acceptable. However, the dust and debris which builds up on external
crusher drive surfaces coupled with a general inaccessibility of
the drive elements in the lower portion of the crushers makes it
difficult to maintain the drives of gyratory crushers.
SUMMARY OF THE INVENTION
It is therefore an object of the invention to provide a gyratory
crusher with a drive for a gyratory crusher head which drive located
away from discharging crushed materials.
It is a further object of the invention to provide a gyratory crusher
with a gyratory drive which is readily accessible for maintenance
operations.
In accordance with the invention, a gyratory crusher includes a
stationary bowl assembly disposed centered on a crusher axis, and
a crusher head assembly having a conical crusher head disposed for
gyratory motion against a concave crushing liner of the bowl assembly.
The crusher head includes a plurality of circumferentially evenly
spaced head support members which extend radially through an annular
material flow path region of the crusher. A gyratory drive mechanism
is disposed annularly about the material flow path region and is
coupled to the head support members to gyrate the head.
In a particular embodiment, the gyratory drive mechanism includes
a circular stationary drive track which is centered on a central
crusher axis and is disposed circumferentially about a crusher housing.
The drive track supports an annular eccentric cam with vertical
and horizontal camming components. The vertical and horizontal camming
components have a resultant which passes through an apex of gyration
of the crusher head. The annular eccentric cam is supported by the
stationary drive track to rotate about the crusher axis along the
drive track.
BRIEF DESCRIPTION OF THE DRAWINGS
The Detailed Description including the description of a preferred
structure as embodying features of the invention will be best understood
when read in reference to the accompanying figures of drawing wherein:
FIG. 1 is a cross-sectional and somewhat simplified side view through
a gyratory crusher showing features of the present invention;
FIG. 2 is a partial top view of the gyratory crusher shown FIG.
1 the gyratory crusher being cut along a central, vertical plane
of symmetry through the crusher;
FIG. 3 is a partial section through an annular drive arrangement
of the crusher in FIG. 1 showing in greater detail features of
the present invention;
FIG. 4 shows schematically an alternate eccentric drive arrangement
in accordance with the invention;
FIG. 5 shows schematically a variation of the alternate drive arrangement
shown in FIG. 4;
FIG. 6 shows a mechanical eccentric drive arrangement as an alternate
embodiment of an annular eccentric member shown in FIGS. 1 and 2;
and
FIG. 7 depicts an overall side elevation of an embodiment of yet
another drive arrangement of the crusher shown in FIG. 1.
DETAILED DESCRIPTION OF THE INVENTION
In reference to FIG. 1 there is shown, in section and somewhat
simplified to highlight particular features of the present invention,
a gyratory material comminution apparatus or cone-type crusher which
is designated generally by the numeral 10. The sectional view of
the crusher 10 shows a crusher frame 12 which generally defines
outside dimensions of the crusher 10. The crusher frame 12 may be
regarded, in general, as a vertically oriented hollow cylinder.
At an upper portion thereof the crusher frame supports a bowl or
concave 14. A bowl liner 15 is replaceably mounted to an inner surface
of the concave 14. The bowl liner 15 is a typical wear item which
may be replaced while the crusher 10 is shut down during maintenance
periods. The concave 14 is supported with respect to the crusher
frame 12 by a bowl support frame or support structure 16. The support
structure 16 the concave 14 and the bowl liner 15 are all centered
on a central vertical axis 17 through the crusher 10. The bowl liner
15 has the shape of a hollow truncated pyramid with a first, circular
upper opening 18 being more narrow than a second, circular lower
opening 19 of the bowl liner 15. The upper opening 18 is a material
feed or intake opening of the crusher 10.
Partially located within the bowl liner 15 and extending through
the lower opening 19 into the space encompassed by the bowl liner
15 is a crusher head 25 of the crusher 10. The crusher head 25
is generally of a conical shape, having in a preferred embodiment
a flattened top or top plate 26. A crusher mantle 27 is replaceably
mounted to the crusher head 25 to constitute an outer surface of
the crusher head 25. The mantle 27 constitute conically upward facing
crushing surfaces of the crusher head 25. The crusher head 25 is
generally disposed along the central vertical crusher axis 17. However,
a central crusher head axis of symmetry or head axis 29 is disposed
and supported at an angle of deviation ("a") with respect
to the central vertical crusher axis 17. The central vertical crusher
axis 17 and the head axis 29 intersect at a certain point or an
apex of gyration 30 simply referred to as an apex 30. The apex
30 is shown to lie in the described embodiment centrally above the
crusher 10. During the operation of the crusher 10 the crusher
head 25 will gyrate about the apex 30 with respect to the concave
14.
The crushing operation is affected by a correct spacing between
the crusher head 25 particularly the mantle 27 and the bowl liner
15. Wear occurring on the respectively facing mantle 27 and the
bowl liner 15 tends to increase an originally correct spacing. Consequently,
periodic corrective adjustments of the spacing between the mantle
27 and the bowl liner 15 are regarded to be standard routines. The
concave 14 has for such purpose external threads 31 which permit
the axial position of the bowl or concave 14 to be adjusted in a
step-less up or down adjustment by rotating the concave 14 about
the central vertical axis 17 with respect to the crusher frame 12
and particularly with respect to the bowl support structure 16.
In distinction over other known bowl support structures which typically
feature internal threads to match with external threads on respective
bowls, the present bowl support structure 16 has peripherally spaced
openings 32 through which extend inwardly toward the concave 14
a plurality of thread lugs 33. The thread lugs 33 may be mounted
or fastened in any of a number of known ways, such as by typical
machine screws or bolts and nuts, to a corresponding arrangement
of external mounting ears 34 also spaced about the cylindrical
periphery of the support structure 16 according to the pattern of
the openings or apertures 32. The peripheral pattern of the apertures
32 and the mounting ears 34 is a helically advancing and peripherally
equally spaced repetition of the combination of one of the apertures
32 and one of the mounting ears 34. A pitch of the helical pattern
of the apertures 32 and mounting ears 34 corresponds to a pitch
of the external threads 31 of the concave 14. Therefore, as one
of the thread lugs 33 is inserted through each respective one of
the apertures 32 and is locked or fastened to the respective one
of the mounting ears 34 the plurality of inwardly extending thread
lugs 33 form in their totality internal threads of the support structure
16. The thread lugs 33 are discrete items. Thus, the helical advance
or pitch of the thread lugs 33 may appear to be a multiple of the
pitch of the threads 31 on the concave 14 yet be in fact be the
same predetermined pitch as that of the threads 31. The thread lugs
33 complement in shape thread grooves of the threads 31. The thread
lugs 33 consequently engage the external threads 31 of the concave
14 to retain the concave vertically in an adjusted vertical position
with respect to the crusher head 25. The adjusted vertical position
of the concave 14 with respect to the crusher head is precisely
adjustable by rotation of the concave 14 with respect to the crusher
frame 12 and about the vertical central crusher axis 17.
A not immediately apparent advantage of the thread lugs 33 in lieu
of conventional threads would be noted during a maintenance shut
down, when the bowl liner 15 and the mantle 17 may need to be replaced
because they have worn beyond tolerable limits. When such replacement
becomes necessary, typically the concave 14 would be threaded out
of the support structure until the concave 14 is free of the support
structure and may be lifted by a crane (not shown). The presently
described structure simplifies removal of the concave 14 from the
support structure 16. The concave 14 may, for example, be hooked
up to a cable and suspended by a crane (not shown), whereupon the
thread lugs 33 are disengaged from the threads 31 of the concave
14. A disengagement of the thread lugs 33 may occur simply by loosening
and withdrawing the thread lugs 33 from their engaging positions.
The thread lugs 33 may of course be completely removed from the
support structure 16 to be replaced prior or during reassembly of
the concave 14 to the support structure 16. The removal or disengagement
of the thread lugs 33 totally frees the concave 14 from the support
structure 16 and permits the concave 14 to be raised with respect
to and lifted from the crusher 10. The ability to lift the concave
14 in a straight upward lifting motion from the crusher avoids a
tedious job of rotating the concave 14 about the central vertical
axis 17 to slowly retract the concave 14 from its lowermost position
prior to removing it from the crusher 10. Such slow removal process
becomes particularly aggravated when the bowl liner 15 has worn
over its useful life cycle and the concave 14 has been adjusted
downward on its threads possibly numerous times. Thus, without removing
the thread lugs 33 several turns of the concave 14 with respect
to the support structure 16 would become necessary to unthread and
free the concave 14 from the grip of the support structure 16.
In the described contemplated embodiment, the thread lugs 33 have
a substantially rectangular engaging or active shape. It should
be understood that other shapes may be equally effective and desirable
to use in engagement with the external threads 31 on the concave
14. Also, for simplicity and in accordance with an initially contemplated
embodiment, the thread lugs 33 are described and shown as fastened
to the mounting ears 34. Advantages of such a structure reside in
what may be considered simplicity and convenience of manufacture.
It may, however, become desirable to pivotally or slidably assemble
the thread lugs 33 to the mounting ears 34. Pursuant to such a modification
retraction provisions indicated by an arrow may be used to slide
most or all of the thread lugs 33 outwardly to further decrease
the time needed in preparation for lifting the concave 14 from the
crusher 10. Time may further be saved when the concave 14 with a
newly mounted bowl liner 15 is reassembled to the crusher 10. The
concave 14 may simply be lowered into the support structure 16 until
the proper spacing with respect to the crusher head 25 is achieved,
whereupon the thread lugs 33 are engaged with the threads 31 of
the concave 14 and are secured with respect to the support structure
16.
Included conical angles of the cones of the bowl liner 15 and the
crusher mantle 27 are such that an annular space of a crushing chamber
35 between adjacent surfaces of the bowl liner 15 and the crusher
mantle 27 generally decreases downwardly. A remaining annular gap
at the lower opening 19 of the bowl liner 15 constitutes an annular
material discharge opening 36 from the crushing chamber 35. During
the operation of the crusher materials are fed into the crushing
chamber 35 through the intake opening 18 and progress downwardly
through the annular crushing chamber 35 being reduced in size through
repeated crushing contacts between the adjacent walls of the bowl
liner 15 and the crusher mantle 27.
A tramp iron relief may be provided by a plurality of preloaded
compression springs 37. The springs 37 are equally spaced about
the outer periphery of the crusher frame 12 and function to urge
the support structure 16 downward against the crusher frame 12.
The amount of pre-compression or preload on the springs 37 sets
the working limit between the mantle 27 and the bowl liner 15. When
the working limit is exceeded by non-crushable material, such as
a piece of tramp iron, the concave 14 is urged upward and away from
the crusher frame 12 by the gyrating action of the crusher head
25 thereby temporarily widening the spacing between the mantle
27 on the crusher head 25 and the bowl liner 15 of the concave 14.
The spacial relief provided avoids a peak increase in crushing forces
which would tend to structurally damage the crusher 10. The springs
37 are held under compression between the crusher frame 12 at one
end and a movable load plate 38 at the other. A compressive downward
force exerted by the compressed springs 37 against the respective
load plate 38 is transferred to the support structure 16 of the
concave 14 by a plurality of peripherally spaced rods 39.
The crusher head 25 is supported by a spider arm cradle 40. The
spider arm cradle 40 is itself supported by, and mounted for gyratory
movement onto, a gyratory drive arrangement 41 which is annularly
disposed about a lower portion 42 of the crusher frame 12. In the
embodiment of the gyratory drive arrangement 41 as shown in FIGS.
1 2 and 3 the lower portion 42 of the crusher frame 12 supports
an annular drive track 43 which extends peripherally about the crusher
frame 12. The drive track 43 may be an integrally manufactured part
of the crusher frame 12 as shown, or the drive track 43 may be
manufactured separately of the crusher frame 12 and mounted externally
of the crusher frame 12 onto the crusher 10 in an assembly operation.
Within the drive track 43 there is rotatably supported a double
eccentric, gyratory drive ring 45. Though the drive track 43 may
be considered part of the somewhat cylindrical crusher frame 12
the drive track 43 is desirably located externally of the generally
cylindrical structure of the crusher frame 12 hence away from crushed
materials which would generally discharge within the confines of
the crusher frame 12. An outer cylindrical bearing surface 46 of
the drive ring 45 is concentric with the central vertical crusher
axis 17 and supports rotation of the drive ring 45 centered on the
axis 17. Horizontal and vertical camming movements are supported
by, respectively, horizontal and vertical eccentric surface elements,
namely a radial camming surface 47 and an axial camming surface48.
The horizontal and vertical camming movements may be represented
by horizontal and vertical motion or displacement vectors. The horizontal
and vertical motion vectors change cyclically in magnitude and direction.
As the drive ring 45 is rotated about the central vertical axis
17 the radial and axial camming surfaces 47 and 48 support outer
spider arm ends 49 of the spider arm cradle 40 in circular motion
to revolve about a gyratory motion axis 50 which extends through
the apex 30. Changes in radial and vertical distances of the radial
and axial camming surfaces 47 and 48 represent, respectively, horizontal
and vertical components of such cyclic movement of the spider arm
ends 49 about their respective axes 50. The deviation angle "a"
of the head axis 29 is established by the combination of a horizontal
camming movement "H1-H2" and a vertical camming movement
"V2-V1", as best seen FIG. 3 showing a maximum excursion
of the crusher head 25 toward the right, as is also the position
of the crusher head 25 in FIG. 1. The measurements "H1 V1
H2 V2" are taken between an intersection of the respective
camming surfaces and the outer cylindrical bearing surface 46 and
a base surface 51 of the drive ring 45.
FIG. 2 is a partial top view of the crusher 10 shown in FIG. 1
and depicts a particular embodiment wherein a single revolution
of the drive ring 45 about the central vertical axis 17 subjects
each of the spider arm ends 49 correspondingly to a full gyration,
namely a complete cycle of circular motion about its respective
axis of revolution 50 with respect to the apex 30. The drive ring
45 may be driven in any of a number of ways, such as by a countershaft
52 connected to a conventional power plant or power source (not
separately indicated). The countershaft 52 as a working end of a
power input or power source is coupled through a typical drive pinion
53 to engage a complementary drive gear 54 which may be disposed
on an upper surface 55 of the drive ring 45 for example. The top
view or plan view also shows the spider arm cradle 40 being formed
by spider arms 56 being spaced peripherally by an angle of sixty
degrees, such that six spider arms 56 form the complete cradle for
supporting the crusher head 25. Instead of a single camming cycle
being formed to correspond to a full revolution of the drive ring
45 it may be considered to form a more complex camming surface which,
for example, provides 1/6 deflection cycles between each 60 degrees
of the altered drive ring (not shown). In the latter example, the
linear speed of advance of the drive ring would be reduced to one-sixth
of that of the drive ring 45 to obtain the same gyrating rate of
the crusher head 25. Camming forces would necessarily be increased
over those generated by driving the drive ring 45.
The outer bearing surface 46 and the base surface 51 may be supported
for rotation on the drive track 43 by thrust bearings 58 and 59
in the radial and vertical directions, respectively. One alternative
to using roller type thrust bearings 58 and 59 may be the use of
lubrication oil supported bearing surfaces against corresponding
bearing surfaces on the drive track 43. In particular reference
to FIG. 3 the spider arm ends 49 may also be supported against
the drive ring 45 by roller bearing assemblies 63 and 64 or the
spider arm ends 49 may be disposed in the alternative against the
respective radial and axial camming surfaces 47 and 48 as oil lubricated
sliding cam follower ends. The radial and axial camming surfaces
47 and 48 are shown to be in a position wherein the respective crusher
head 25 (see FIG. 1) would have gyrated to its open side setting.
FIGS. 4 and 5 are schematic diagrams of crusher heads 25 being
supported by, as examples of choices within the scope hereof, four
spider arms 56 and six spider arms 56 respectively. In a crusher
design application, the number of spider arms 56 forming a respective
spider arm cradle may vary depending on the size of the crusher
10 and the forces which must be supported by the respective gyratory
drive arrangement 41. It may be desirable to support a crusher head
25 of a relatively large crusher by a cradle formed of eight, nine
or ten spider arms 56. Of course, the size of the crusher 10 may
not be the only factor decisive of the number of spider arms 56
used to form a spider arm cradle. The shape, section, and supportive
strength of the spider arms 56 and expected crushing forces to
be experienced by the crusher 10 may need to be considered. A spider
arm cradle 65 having four spider arms 56 shows a possible variation
of the number of spider arms toward the low end of the number of
spider arms 56 from the already described six spider arm cradle
40. The gyratory motion of a crusher head in a conventional gyratory
or cone crusher would typically be generated by an eccentric which
revolves about an axis of rotation and which gyrates, in turn, a
single shaft of the crusher head at the its speed of rotation. In
the present invention, there may be a single eccentric element,
such as the drive ring 45 (see FIGS. 1 and 2), which imparts eccentric
rotational motion to all of the spider arms 56 and at a phase shift
in accordance with their peripheral spacing about the crusher head
25 whereby the crusher head 25 is gyrated.
In reference to FIGS. 4 and 5 a gyration of the crusher head 25
which is the same as the gyration generated by the described drive
ring 45 (in FIG. 2) may be generated by a plurality of individual
rotational motion generators 66 all of which operate at the same
rotational speed, and which eccentrically drive the each of the
spider arms 56 to revolve about its respective axis of revolution
50. Thus, each of the motion generators 66 is centered on a respective
one of the axes 50 and all motion generators 66 face the apex 30.
In the schematic top views, a top or uppermost angular eccentric
position of the spider arm 56 with respect to the motion generator
66 corresponds to an outermost position of the elliptic face of
the motion generators 66 away from the apex 30. The phase of rotation
or the angular position each of the spider arms 56 in its respective
circular path of revolution about the respective axis 50 is shifted
with respect any other one of spider arms 56 by an angle that corresponds
to the peripheral separation angle of the respective two spider
arms 56 with respect to each other.
In reference to FIG. 4 synchronization between the individual
rotational motion generators 66 is depicted by double-headed arrows
68. The arrows 68 schematically indicate bi-directional feedback
communication links 68 between adjacent ones of the motion generators
66. The motion generators 66 for example, may be hydraulic motors
66. The schematically indicated feedback communication links 68
may represent one or more hydraulic fluid lines, or even a combination
of hydraulic fluid lines and electrical signal lines to direct or
apply hydraulic driving fluid and electrical position signals. In
the example of the feedback communication links being hydraulic
fluid lines and electrical signal lines, each of the hydraulic motors
66 may be equipped with a position indicator, which may be a known
electro-optical position indicator. A power control system 69 may
be coupled to drive and control all four of the hydraulic motors
66 as indicated by the double-headed arrow 70. In the present example,
the schematic symbol of the arrow 70 represents hydraulic fluid
feed and return lines, as well as electrical signal lines for communicating
an angular position of each of the respective hydraulic motors 66
to the power control system 69. The power control system 69 synchronizes
the speed and angular position of each of the hydraulic motors 66
with respect to each other, such that the phase or angular position
of each of the spider arms 56 remains the same with respect to all
other spider arms 56.
In FIG. 4 a first hydraulic rotational motion generator 66 (disposed
in a "three o'clock" position coupled to the arrow 70)
has rotated the respective spider arm 56 to a top position at an
instance in a gyratory cycle when the crusher head 25 is in a depicted
position which corresponds to that of the crusher head 25 in FIGS.
1 and 2. An exemplary direction of rotation of the motion generators
66 is indicated by arrows 72. To generate an exemplary gyratory
motion of the crusher head 25 the direction of motion of all rotational
motion generators 66 must be the same as viewed from the apex 30.
Looking down on the crusher head 25 in FIG. 4 a second of the motion
generators 66 (disposed in a six o'clock position, clockwise displaced
by ninety degrees from the first motion generator) shows a position
of the corresponding spider arm 56 which leads that of the spider
arm associated with the first motion generator by ninety degrees.
Correspondingly, the position of the spider arm 56 of a third motion
generator 66 in the nine o'clock position, opposite the first motion
generator 66 is in a lowermost position being shifted in its positional
phase by one-half revolution of the eccentric motion of the respective
motion generator 66. The four spider arms 56 of the spider arm cradle
65 in FIG. 4 are, as described, peripherally spaced at right angles
or ninety degrees of arc, and a corresponding positional phase shift
of adjacent eccentric motion generators is also ninety degrees of
arc.
FIG. 5 shows similarly the six-spider-arm cradle 40 which would
be of substantially the same structure as the spider arm cradle
40 already described with respect to FIGS. 1 and 2. The six spider
arms 56 are, however supported by six individual eccentric motion
generators 66. The motion generators 66 in FIG. 5 are also equally
spaced about the periphery of the crusher 10. A power control system
75 is shown to be coupled by a drive and communications link 76
to control the motion of the eccentric motion generators 66. FIG.
5 also illustrates that the rotation of all of the eccentric motion
generators 66 is in the same direction as viewed from the apex 30
as indicated by the directional arrows 72. Also, the speed of all
six of the eccentric motion generators 66 must remain synchronized
with respect to each other. Double headed arrows 77 between each
two adjacent motion generators 60 illustrate interactive communications
or feedback links 77 between the motion generators 66 which synchronize
their rotational motion with respect to each other. The eccentric
motion generators may, in instead of already described hydraulic
motors be electric motors 66 or other eccentric motion generators
66.
FIG. 6 illustrates a mechanical embodiment of an eccentric motion
generator 66 which may function in the manner described in reference
to FIGS. 4 and 5. A lower portion 81 of the crusher frame 12 is
modified to support a drive gear 82. The drive gear 82 is depicted
as being rotatably supported on bearings 83 and 84 to rotate peripherally
about the crusher frame 12. The bearings 83 and 84 may be roller
bearings arranged to support vertical and radial force vectors.
The drive gear 84 may be driven along its outer periphery, such
as by drive teeth 85 which become engaged by a drive pinion 86 mounted
on a horizontally and radially disposed drive countershaft 87. The
countershaft 87 is chosen as a typical input from, and represents
an output shaft of, a power source 87 to operate the crusher 10.
The drive gear 82 drives a power input gear 89 of each of the peripherally
spaced, mechanical eccentric motion generators 66. A second set
of drive teeth 91 may be disposed conveniently adjacent a sloped
support flange 92 which supports a drive shaft 93 of the eccentric
motion generator 66. The drive shaft 93 is centered on the axis
of revolution 50 of the eccentric motion generator 66. The drive
shaft 93 is journalled for rotation within the flange 92 and is
drivably coupled on an upper side of the flange 92 to an eccentric
drive plate 96. The drive plate 96 may be supported against the
flange 92 by a thrust bearing 97 which may be a roller bearing.
The thrust bearing 97 would be chosen to withstand the forces of
the crushing operation that are transmitted through the respective
spider arm 56 and through a spherical or ball-type toggle link 98
which may be seated within a complementarily shaped socket 99. In
that generating crushing forces are ultimately transmitted to and
supported by the flange 92 of the crusher frame 12 support gussets
or ribs 100 desirably strengthen the support flange 92 on both sides
closely adjacent the eccentric motion generators 66. The ball and
socket type structure depicted in FIG. 6 is shown in a simple manner
for illustrative purposes to emphasize an eccentric offset ("e")
which is the radius by which the respective spider arm end 49 revolves
about the axis 50. Depending on the size of the crusher 10 and
the expected magnitude of crushing forces, the size and, hence,
the contact area of the ball link 98 and the corresponding spherical
cavity 99 would be increased over the relatively small spherical
size of the ball 98 and socket 99 in FIG. 6. With such an increase
in bearing area of the ball 98 (the spherical segment of the ball
on the drive plate 96) and corresponding socket 99 it is understood
that the diameter of the drive plate 96 may correspondingly be increased.
End surfaces 101 of the spider arm 56 are chamfered or sloped away
from the drive plate 96 to provide clearance for the rotational
and resulting gyratory pivotal movement of the spider arms 56 as
all of the spider arms 6 are set into motion. Of common departure
from the known art in general, is the location of the eccentric
motion generators 66 being supported outwardly toward the periphery
of the housing or frame 12 of the crusher 10. This is believed to
be an advantageous departure from the structures of other existing
gyratory crushers. While, in general, gyratory crushers, such as
cone crushers, are driven by a countershaft which radially extends
to a drive gear disposed generally centrally below the crusher and
radially within the annular discharge region of such crushers, the
disclosed eccentric motion generating mechanisms are disposed peripherally
about such discharge region. The spider arms 56 extend through the
material discharge region to impart the gyratory motion to the crusher
head 25. Thus the described eccentric drive ring 45 and the individual
eccentric motion generators 66 are disposed externally of the crusher
frame 12 and away from the annular discharge region about a periphery
105 of the crusher head 25. Advantages in addition to allowing ready
access to the eccentric motion generators 66 or to the drive ring
45 are a distribution of crushing forces to the periphery of the
crusher 10 particularly to the base of the frame 12. A further
advantage as a relatively low crusher profile, as compared to known
crushers which have a crusher drive train beneath the crusher frame.
A comparatively low profile of the crusher 10 in comparison to
some known gyratory crushers may be recognized from FIG. 7 showing,
somewhat simplified, an overall side elevation of the crusher 10.
A material intake hopper or box 110 may be mounted above the upper
opening 18 of the crusher 10. The compression springs 37 which hold
the concave 14 against the crusher frame 12 prominently encompass
an upper part of the crusher frame 12. At the lower portion 42 of
the crusher frame 12 the gyratory drive ring 45 extends above the
annular drive track 43. Pursuant to the embodiment in FIG. 7 the
exposed portion of the gyratory drive ring 45 has a plurality of
V-belt grooves 111. The frame 122 is extended or coupled to support
frame extension 112 which functions as a motor mount. A power source
or power plant 114 such as an engine or an electrical drive motor
is mounted to and supported by the support frame extension 112.
If a chosen power plant 114 and its position on the support frame
extension 112 results in a horizontal power take-off, a right angle
drive conversion box 115 may be coupled to the power plant 114 or
may also be supported by the support frame extension 112. The right
angle drive conversion box 115 or a direct vertical shaft power
output 115 of the power plant 114 drives a drive pulley or a V-belt
drive sheave 116 about a vertical axis. One or more drive belts
118 for example, a selected number of V-belts 118 depending on
power requirements, couple a power input from the power plant 114
via the sheave 116 directly to the gyratory drive ring 45 of the
crusher 10. The drive belts 118 extend over both the drive surfaces
of the drive sheave 116 and the drive ring 45 and hence couple the
drive ring 45 to be driven at the same surface motion of the drive
sheave. Belt tightening adjustments may be made in a routine manner
by sliding the power plant 114 with the drive sheave 116 in a direction
transverse to the axes of the drive sheave 116 and the crusher 10
as indicated by the arrow 119.
As will be realized from the above embodiments of the gyratory
crusher the described embodiments are illustrative and specific
examples of apparatus to which the invention applies. Various other
changes and modification to the described apparatus may be made
in view of the above description without departing from the spirit
and scope of the invention which is defined by the claims below. |