Abstrict A cone crusher characterized by a frame having a completely fabricated
construction, an anti-spin mechanism and an improved crusher setting
indicator is disclosed. The frame of the structure, which is composed
solely of pre-formed and/or forged members, includes a number of
tubular members, a number of annular members and a number of ribs,
all of which are welded together to provide a rigid, strong frame.
The anti-spin mechanism is characterized by the use of a unidirectional
valve and a spring loaded ball valve, thereby permitting the rotation
of the mantle of the crusher in one direction while barring rotation
of the mantle in the opposite direction unless a force exceeding
a pre-selected magnitude is applied to the mantle. The crusher setting
indicator, which is used to determine the distance between the moveable
mantle and the stationary concave of the crusher includes a rod
supported by the crusher, the rod abutting the cone support bearing
seat of the crusher, the position of which seat is directly related
to the position of the mantle. A pinion gear is coupled to the rod
and the orientation of the gear is used to provide an indication
of the distance between the mantle and concave.
Claims Having thus described the invention, what is claimed and desired
to be protected by Letters Patent is:
1. A crusher setting indicator for a cone crusher, which crusher
includes a movable mantle and a stationary concave, comprising:
a rod, supported by said crusher, arranged for linear movement
along a line, the position of said rod along said line of linear
movement being directly related to the position of said mantle along
said line;
said crusher further including a center hub having an axially extending
path formed therein, said rod being positioned within said path
wherein said path is a crusher lubrication path and said rod is
tubular, said rod thereby being adapted to form a portion of said
lubrication path;
said crusher further including a cone support bearing seat arranged
for movement along said line wherein one end of said rod is in abutting
relationship with said seat;
biasing means coupled to said rod for biasing said rod into said
abutting relationship with said seat; and
means responsive to the position of said rod along said line for
providing an indication of the distance, along said line, between
said mantle and said concave.
2. A crusher setting indicator according to claim 1 wherein said
biasing means comprises a piston ring.
3. A crusher setting indicator according to claim 1 wherein said
rod bears a plurality of teeth along at least a portion of the length
thereof and wherein said responsive means is a gear arranged for
rotation about a shaft, at least a portion of the periphery of said
gear bearing a plurality of teeth, said gear teeth and said rod
teeth being positioned for engagement with one another.
Description This abstract is not to be taken either as a complete exposition
or as a limitation of the present invention, the full nature and
extent of the invention being discernable only by reference to and
from the entire disclosure.
BACKGROUND OF THE INVENTION
This invention relates to cone crushers and more particularly to
such crushers which have fabricated upper and lower main frames.
In addition, this invention relates to such cone crushers which
include anti-span mechanisms and crusher setting indicators.
Cone crushers, which are devices well known in the art, are devices
which are adapted to receive large pieces of hard material such
as, for example, large chunks of rock and to reduce them to a large
number of smaller pieces which are of a generally uniform size.
The crushers which are presently widely used in the concrete and
aggregate industry have numerous characteristics which make them
less than ideal. For example, such crushers must have extraordinarily
strong main frames due to the fact that they are subject to extreme
mechanical stresses. For this reason, among others, such crushers
have generally been provided with cast frames. Although such cast
frames have generally proved to be of sufficient strength, the cost
of their manufacture is quite high and they are therefore, from
an economic point of view, less than completely satisfactory. In
an effort to overcome this negative aspect it has been proposed
to fabricate the lower portion of the main frame of such a crusher
from pre-formed components rather than to cast it and to thereby
obtain substantial savings. An example of such a cone crusher which
includes a fabricated lower main frame portion is provided in U.S.
Pat. No. 3150839. It is noted, however, that even this patent
teaches a crusher main frame structure which includes cast members,
in particular, this patent teaches a structure utilizing a cast
center hub. The industry, recognizing the advantages of fabricated
main frames for crushers has attempted to provide main frame structures
which are completely fabricated, that is, contain only plate and
forged members and contain no cast members. An example of a crusher
frame which is constructed from only fabricated members is provided
by U.S. Pat. No. 3843068 which is fabricated solely from pre-formed
components which are welded together. Such structures, although
providing definite advantages over the earlier cast structures are
nevertheless not completely satisfactory in that they frequently
require great numbers of components to fullfill their function.
For example, the last noted patent includes an adapter plate for
permitting the mating of the center hub with the countershaft which
houses the required motor drive shaft. Clearly, this results in
less than a completely satisfactory solution to the problem because
a greater number of prefabricated sections requires a greater number
of welds. This, in turn, provides the opportunity for unsatisfactory
welds and results in increased expense in that each of the welds
must be (or should be) inspected either by X-ray or ultra-sonic
techniques or both.
As indicated above, the function of a crusher is to provide, for
subsequent use, stones, crushed rock, etc. of a uniform size. Clearly,
therefore, it is important to be able to determine, prior to operation
of the crusher, the magnitude of the crushed material which will
be provided by the crusher unit, that is, the crusher setting. Presently
known crusher setting indicators are not, however, completely satisfactory
in that they are either mechanically complex and expensive or they
do not provide information regarding the size of the material to
be provided by the crusher with a desired degree of accuracy. It
is, of course, possible to accurately and inexpensively determine
the crusher setting by measuring the size of the material after
it passes through the crushing chamber and is emitted from the crusher
but such information is obviously of less utility than is knowledge
of the crusher setting prior to operation of the crusher.
Cone crushers of the type here under discussion include a gyratory
member generally referred to in the art as a mantle. Due to the
construction of the crusher, the gyrating mantle has a tendency
to rotate in a first direction when the crusher is not under load,
that is when the crusher is not in the process of crushing material.
Further, the mantle tends to rotate in a second direction, opposite
to the first direction, when the crusher is under load. As is well
known in the art, rotation of the mantle in the first (no load)
direction is to be avoided because such rotation can cause additional
and extensive wear to the expensive mantle. It is therefore quite
common in the crusher art to provide what is frequently referred
to as an anti-spin mechanism. The mechanisms presently known frequently
are in the form of devices which absolutely bar the rotation of
the mantle in the first direction while permitting the mantle to
freely rotate in the second direction. The utility of such mechanisms
has proved to be less than completely satisfactory because absolutely
barring the rotation of the mantle in the first direction, may,
under conditions where the mantle is being urged in the first direction
with sufficient force, result in the destruction of components of
the crusher.
SUMMARY OF THE INVENTION
It is therefore an important object of the present invention to
provide an improved cone crusher setting indicator by means of which
the aforesaid drawbacks and disadvantages may be most efficaciously
avoided.
It is another object of the instant invention to provide a crusher
setting indicator for a cone crusher structure which is mechanically
simple and inexpensive.
It is yet another object of the instant invention to provide a
crusher setting indicator for a cone crusher which is more accurate
than presently known indicators.
Generally speaking, the objects of the instant invention are attained
by the provision of a crusher setting indicator for a cone crusher,
which crusher includes a moveable mantle and a stationary concave,
comprising a rod, supported by the crusher, arranged for linear
movement, the position of the rod along the line of linear movement
being directly related to the position of the mantle along the line,
and means responsive to the position of the rod along the line for
providing an indication of the distance, along the line, between
the mantle and the concave.
The foregoing and other objects of features of the present invention
will be more clearly understood from the following detailed description
thereof when read in conjunction with the accompanying drawings,
in which:
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a cross-sectional plan view of the cone crusher of the
instant invention;
FIG. 2 is a detailed cross-sectional plan view of the anti-spin
mechanism of the instant invention;
FIG. 2A is a schematic representation of the anti-spin mechanism
shown in FIG. 1;
FIG. 3 is a plan view taken along lines 3--3 of FIG. 1;
FIG. 4 is a cross-sectional plan view taken along lines 4--4 of
FIG. 1;
FIG. 5 is a detailed cross-sectional plan view of the crusher setting
indicator of the instant invention;
FIG. 6 is a detailed cross-sectional plan view of the sealing arrangement
of the instant cone crusher; and
FIG. 7 is a cross-sectional plan view taken along lines 7--7 of
FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to FIG. 1 there is illustrated the cone crusher of
the instant invention. The crusher includes a frame which is in
two portions, that is, upper and lower main frame portions, these
portions being bolted together to form the crusher main frame. Turning
first to the upper main frame portion, there is illustrated a feed
hopper (although feed hoppers are generally considered by the art
to be separate from, and not form part of, a crusher frame, the
feed hopper herein will be described as if it formed part of the
upper main frame portion) generally indicated at 1 which includes
a fabricated tubular member 3 which member may be fabricated from
bend rolled steel plate. A fabricated member 5 which has the general
cross-sectional configuration of a truncated cone and a fabricated
member 7 which also has the general cross-sectional configuration
of a truncated cone are both welded, at their upper peripheries,
to the member 3. The members 5 and 7 are also welded to one another
along their contiguous lengths, it being noted that the member 5
is longer than the member 7. A fabricated tubular member 9 is welded
at its upper periphery to the lower periphery of the truncated member
7 and to the side of the member 5. The tubular member 9 is further
welded, at its lower periphery, to an annulus 11 the combination
of the tubular member 9 and annulus 11 having an L-shaped cross-sectional
configuration. The annulus 11 is formed with a plurality of holes
therein and it is thereby adapted to be firmly affixed to an annulus
13 which is formed with a plurality of countersunk threaded holes,
by any conventional means, for example, by screws such as the one
indicated at 15.
An upper crushing member or concave 17 having the general cross-sectional
configuration of a truncated cone is cast from an extremely hard
and long wearing material such as, for example, manganese steel,
and it is formed with a plurality of gripping or hook members, one
of which is indicated at 19. The concave 17 is maintained in position
by a plurality of gripping members 21 which pass through apertures
20 formed in the annulus 13 which gripping members 21 may have
any desired configuration. In the embodiment illustrated in FIG.
1 the gripping members 21 each have a "T" shaped cross-section
although a member having a "J" shaped cross-section could
also be utilized. Conventional tightening nuts, such as those indicated
at 22 serve to draw the gripping members 21 upwardly, thereby drawing
the concave 17 upwardly to its desired position. An annulus 23
oriented so as to be parallel to both the annuli 11 and 13 is positioned
in the vicinity of the lower end of the concave 17.
A plurality of gussets or ribs 25 which are oriented orthogonally
with respect to the annuli 13 and 23 are welded to the annuli 13
and 23 so as to form a rigid support therebetween. The ribs 25 are
equally spaced circumferentially and there may be, for example,
16 such ribs spaced 22.5.degree. apart, as clearly seen in FIG.
4. A plurality of the ribs 25 are formed with apertures 27 therethrough
so as to facilitate the lifting of the upper portion of the fabricated
main frame of the crusher when separation of the upper and lower
main frame portions is desired. As indicated above, the crusher
may include 16 of the ribs 25 and, for example, four of the ribs,
spaced 90.degree. apart, might be formed with apertures such as
the one indicated at 27.
A fabricated tubular member 29 which may be formed of bend rolled
sheet steel, is welded at its upper periphery to the annulus 23.
Apertures such as the one indicated at 33 are formed at various
locations about the periphery of the tubular member 29 which apertures
may be blocked by, for example, hinged doors such as the one indicated
at 35 so that access may be had to the interior of the crusher when
such access is required.
A number of ribs, for example, four, most clearly shown in dotted
lines in FIG. 4 are uniformly spaced about the circumference of
the upper main frame portion of the crusher. The ribs 30 which
have "U" shaped cross-sectional configurations (the open
ends of the "U" abutting the tubular member 29 and the
closed end of the "U" extending in a radially outward
direction) are welded, at their upper peripheries, to the annulus
23. The ribs 30 are also welded, at their open ends, to the tubular
member 29. A tubular wear liner 31 which may be made of a long
wearing material such as low carbon steel and which may be formed
by rolling, is tack welded at a number of points to the radially
inward surface of the tubular member 29. The wear liner 31 serves
to reduce the wear of the tubular member 29 which would be caused
by the action of the crushed material being processed by the crusher
unit and, of course, the liner may be removed and replaced when
necessary. A number of ribs or gussets 32 for example, eight such
gussets, are welded to the annulus 23 the tubular member 29 and
the wear liner 31 so as to combine the annulus 23 the member 29
and the liner 31 into a rigid structure. A horizontal annulus 37
is welded to the lower peripheries of the tubular member 29 and
the "U" shaped rib 30. The annulus 37 is formed with a
plurality of apertures 38 formed therein through which bolts may
be passed for attaching the just described upper main frame portion
to the lower main frame portion of the cone crusher, which lower
portion will be described in detail below.
Turning now to a description of the lower main frame portion and
referring to FIG. 1 it is seen that the lower main frame portion
includes a forged steel center hub 41 which has an annular shoulder
43 formed at the upper end thereof. An annulus 45 (which is illustrated
in FIG. 7 and which will be described in greater detail below) is
welded to the hub 41 at the shoulder 43 and a fabricated tubular
member 47 which may be, for example, of bend rolled steel plate,
is welded to the annulus 45 at the outer periphery thereof. An annulus
49 oriented to extend orthogonally relative to the member 47 is
welded thereto interjacent the ends thereof. The annulus 49 is formed
with a plurality of apertures 51 being so located as to be in alignment
with the apertures 38 which extend through the annulus 37. It may
therefore be seen that the annuli 37 and 49 may be rigidly attached
to one another by, for example, a bolt and nut combination such
as indicated at 53 thereby accomplishing the connection of the upper
and lower main frame portions.
A plurality of ribs or gussets 61 for example, three (most clearly
seen in FIG. 3), are welded to the forged center hub 41 and to a
fabricated tubular member 63 which may be formed of bend rolled
sheet steel. The tubular member 63 extends orthogonally relative
to the annulus 49 and the member 63 is welded, at its upper periphery,
to the annulus 49. In addition, the ribs 61 are welded to the annulus
45 to the tubular member 47 and to the annulus 49 thereby imparting
substantial strength and rigidity to the fabricated lower main frame
portion.
A driving mechanism is, as is conventional, provided for the crusher
of the instant invention in a manner which will be explained below
and to this end there is provided, as part of the lower main frame,
a drive shaft housing. The space for the drive shaft housing is
provided by forming, for example, by burning, a circular aperture
in the tubular member 63 the aperture formed extending through
the tubular member 47 and the annulus 45. It will be understood
of course that the annulus 45 may either be provided as a complete
annulus, a portion subsequently being removed therefrom, or, alternatively,
the annulus 45 may originally be formed as a slotted circular plate
(the slot having parallel side walls) as indicated in FIG. 7. A
fabricated tubular member 69 which may, for example, be made of
bend rolled sheet steel extends through the aforementioned circular
aperture and forms the drive shaft housing. The drive shaft, which
is indicated generally at 71 is of any conventional form and may
be used to drive the inventive crusher in any conventional manner.
For example, the embodiment of the invention illustrated in FIG.
1 shows the drive shaft 71 driving the cone crusher by means of
a conventional bevel gear which is indicated generally at 73.
As was noted above with respect to the ribs 61 a number of ribs
67 in this embodiment, two (most clearly seen in FIG. 3), are welded
to the center hub 41 the tubular member 63 and to the tubular member
69. The ribs 67 therefore, also impart substantial strength and
rigidity to the fabricated lower main frame portion and differ from
the ribs 61 only in that the ribs 67 do not extend upwardly to the
annulus 49 as do the ribs 61 the ribs 67 terminating at the drive
shaft housing member 69.
Turning now to a description of the internal structure of the cone
crusher, it is seen that the crusher includes a forged shaft 81
having at least two lubrication paths 83 formed therein. Additional
lubricational paths, such as those indicated at 85 are also formed
in the shaft 81. It is also appropriate to note at this point that
the tubular hub 41 is formed with a stepped bore indicated at 82.
The stepped bore 82 is formed with an internal diameter which is
slightly greater than the internal diameter of the hub 41 in the
lowest portion thereof so as to facilitate the insertion of the
shaft 81 into the center hub 41. Surrounding the shaft 81 which
is stationary during the operation of the crusher, is an eccentric
sleeve 91. The eccentric sleeve 91 which is driven by the drive
shaft 71 through the mechanism of the bevel gear 73 extends upwardly
to a point beyond the uppermost portion of the shaft 81 and downwardly
to a bearing 93 which is in turn supported by the hub 41 the bearing
93 facilitating the rotation of the eccentric sleeve about the shaft
81. To reduce the wear of both the shaft 81 and the eccentric 91
a bearing of relatively soft alloy metal may be positioned between
the adjacent bearing surfaces of the shaft 81 and the eccentric
91. Alternatively, a layer of relatively soft alloy metal, such
as, for example, an alloy including lead, tin and antimony may be
coated onto one or both of the bearing surfaces as is the case in
the embodiment illustrated.
The interior of the tubular shaft 81 serves as a piston chamber,
indicated at 95 and a piston 97 is positioned therein. The piston
97 is actuated by hydraulic fluid which is provided by a mechanism,
not shown, through a conventional tubing and coupling combination,
generally indicated at 99 to a section of conventional tubing indicated
at 101. The tubing 101 together with a conventional hydraulic coupling,
extends through a passage, indicated at 103 formed in the hub 41
and the shaft 81. The tubing 101 extends at its other end to a coupling
105 by means of which it is connected to an accumulator 107. The
accumulator 107 is supported by a frame, indicated generally at
108. The frame 108 is attached to the lower portion of the main
frame by any conventional means such as, for example, a clamp indicated
at 110. It is here appropriate to note that, for reasons which will
be discussed below, a gas containing bag 111 is positioned within
the hydraulic fluid accumulator 107. As previously noted, the interior
of the shaft 81 serves as the piston chamber 95 and as illustrated,
the chamber extends through the bottom of the shaft 81. To prevent
the hydraulic fluid within the chamber 95 from exiting through the
bottom of the shaft 81 a conventional plug or bleeder flange 113
is inserted into the opening in the shaft 81 and the plug 113 is
affixed to the shaft 81 by any conventional means, such as, for
example, the screws shown. An air tube 115 supported at its lower
end by the plug 113 extends into the piston chamber 95 and up to
the bottom of the piston 97. The tube 115 terminates, at its lower
end, in a valve 117 positioned, for protection, in a groove in the
plug 113. In this manner air trapped below the piston 97 may be
released into the atmosphere through the valve 117.
Supported by the piston 97 is a support cone bearing seat 125 which
may be affixed to the piston 97 by any conventional means such as
a plurality of screws, one of which is illustrated. Formed in the
support cone bearing seat 125 is a lubrication passage 127 which
is aligned with the lubrication passage 83 formed in the shaft 81.
Supported by the support cone bearing seat 125 is the support cone
bearing 129 and supported by the support cone bearing 129 is a clutch
housing 131. Supported by and attached to the clutch housing 131
is a support cone 141 which support cone is supported by a circular
shoulder 142 formed at the lower end of the clutch housing 131.
The support cone 141 is in annular abutting relationship with the
eccentric sleeve 91 and the support cone 141 extends downwardly
for almost the entire length of the sleeve 91. To reduce the wear
of both the sleeve 91 and the support cone 141 a layer of relatively
soft alloy metal is coated onto one or both of the bearing surfaces
of the cone 141 and the sleeve 91.
A steel flywheel 148 is connected to the eccentric 91 by, for example,
a bolt such as the one indicated at 152 and the flywheel 148 is
arranged to rotate with the eccentric 91. Connected between the
support cone 141 and the flywheel 148 is a grease filled labyrinth
seal indicated generally at 161 the purpose of which is to prevent
grit such as particles or rock, rock dust, etc. from entering the
internal structure of the cone crusher where such particles would
cause excessive wear. The labyrinth seal includes a plurality of
tubular sealing rings 163. In the embodiment here illustrated, there
are four such rings 163 two of which are upper sealing rings, extending
downwardly from the support cone 141 and two of which are lower
sealing rings, each of which extends upwardly from the flywheel
148. It will be noted that the sealing rings 163 are arranged in
an interlacing relationship so that grease injected into the voids
between the rings 163 will effectively prevent grit from entering
the internal structure of the crusher. As most clearly illustrated
in FIG. 6 one or more grease fittings, indicated at 165 are provided
about the periphery of the labyrinth seal 161 and these fittings
165 are connected, by means of tubing 167 to a port 169 formed
in the radially outwardmost one of the sealing rings 163. A wear
collar 181 which collar may be made of low carbon steel, is welded
to the support cone 141 the collar 181 extending generally in the
area of the upper half of the seal 161. The wear collar 181 thus
prevents damage to the labyrinth seal structure 161 which might
be caused by crushed material, which has passed through the crushing
chamber, striking the sealing rings 163.
Supported by the support cone 141 is a mantle 191 which has the
cross-sectional configuration of a truncated cone. Supported by
the uppermost portion of the mantle 191 is a collar 193 which has
a generally flared tubular or bell-like configuration. The collar
193 forms part of a hydraulic nut assembly, indicated generally
at 195 which assembly will be more fully described below. Supported
by, and attached to, the hydraulic nut assembly 195 is a feed plate
197 which may be made of low carbon steel. The plate 197 serves
to distribute the material provided to the crusher evenly about
the crushing chamber and to protect the uppermost portion of the
internal structure of the cone crusher.
Turning now to a more detailed description of the hydraulic nut
195 it may be seen that a nut 201 is threaded onto the externally
threaded clutch housing 131 forcing the collar 193 downwardly and
thereby urging the mantle 191 into snug engagement with the support
cone 141. To increase the downward force applied by the collar 193
to the mantle 191 a hydraulic pump, not shown, applies, via tubing
203 hydraulic fluid under pressure to a chamber bounded by the
lower portion of the nut 201 and the upper portion of the collar
193. The hydraulic fluid thus urges the nut 201 upwardly and the
collar 193 downwardly. The nut 201 cannot, however, move upwardly
because it is threaded onto the clutch housing 131. The pressure
of the hydraulic fluid thus forces the collar 193 downwardly. When
the system has been pressurized to a desired degree (the collar
urged downward with a predetermined force), a lock nut 205 is threaded
onto the outer periphery of the nut 203 (which nut 203 is threaded
externally as well as internally), until the nut 205 is snug against
the collar 193. At this time the hydraulic pressure may be released
and the nut 205 the nut 201 and the collar 193 will maintain the
mantle in place.
It is appropriate to note at this time that the nut 205 is formed
with a plurality of ears, for example, four, in which axially extending
holes are formed. The holes formed in the ears 207 are so spaced
as to be in alignment with a plurality of countersunk, threaded,
axially extending holes formed in the under-surface of the feed
plate 197 thereby permitting screws, such as the one indicated
at 209 to hold the feed plate in position.
Supported by the support cone bearing seat 125 and connected thereto
by a conventional universal joint 219 such as, for example, a Hooke's
joint, is a shaft 221. The shaft 221 is connected, by means of a
conventional universal joint 223 to an anti-spin mechanism, indicated
generally at 225. The anti-spin mechanism 225 which is most clearly
shown in FIG. 2 includes a hydraulic motor or pump 231. The drive
shaft of the motor is connected, by means of the collar 233 to
the universal joint 223. Fixedly positioned within the space formed
by the feed plate 197 the nut 205 and the clutch housing 131 is
generally cubical hydraulic reservoir 241. As will be understood,
lubricating fluid provided to the cone crusher via the lubricating
passages 83 and 127 fills the open area in which the shaft 221 is
located and, by means of ports (not shown), the interior of the
reservoir 241. Fixedly positioned in any conventional manner within
the lubricating oil filled reservoir 241 are a manifold 243 a check
valve 245 and a relief valve 247 each of which is conventional
and which may be hydraulically coupled in any conventional manner.
For reasons which will be discussed below a length of tubing 249
extends from the manifold to the lower portion of the reservoir
241 to insure a supply of hydraulic fluid (the lubricating oil)
for the operation of the anti-spin mechanism 225. It should be pointed
out, however, that although the instant arrangement illustrates
a manifold located in the upper region of the resevoir 241 an equivalent
structure could obviously be provided by locating the manifold and
motor in the lower portion of the reservoir 241 thereby insuring
an adequate supply of hydraulic fluid for the operation of the anti-spin
mechanism without the need of tubing such as that indicated at 249.
Further, although the check valve 245 and the relief valve 247 are
illustrated as being at opposite sides of the reservoir 241 with
the manifold 243 positioned therebetween, other hydraulically equivalent
configurations could obviously be utilized. For example, an arrangement
wherein the relief valve, the check valve and the manifold are vertically
arranged at one side of the reservoir 241 with the relief valve
being positioned uppermost and the manifold being positioned at
the bottom the the reservoir chamber, would clearly provide an equivalent
structure. The shaft of the motor 231 which is, as previously noted,
coupled to the shaft 221 by means of the universal joint 223 does
not rotate. Rather, the motor 231 is arranged for rotation. The
motor, by means of the motor housing fixedly connected thereto,
is connected directly to the clutch housing 131 and it will therefore
be obvious that the rotation of the clutch housing, the support
cone 141 and the mantle 191 will be directly related to the rotation
of the motor 231. Alternatively, however, it may be desired to attach
the motor housing to a conventional base plate which could, for
example, take the form illustrated in FIG. 2 at 261 and to attach
the base plate 261 to the clutch housing 131 thereby accomplishing
the same end.
Turning now to FIG. 5 there is illustrated, in detail, the crusher
setting indicator of the instant invention. The crusher setting
indicator includes a tubular rod 281 which is located within the
lubrication path 83 formed in the shaft 81 and the rod may be made
of any suitable material, for example, steel. The uppermost portion
of the rod 281 is in contact with the support cone bearing seat
125 and its lowermost portion, indicated at 285 extends into a
lubrication fitting 283 located just below the lowermost portion
of the lubrication path 83. It is appropriate to note at this point
that the rod 281 which is located within the lubrication path 83
is tubular so that the rod itself may serve as a portion of the
path for the lubricating medium. The lower portion of the rod 281
bears (may be formed or fitted with) a series of gear teeth (a rack)
indicated generally at 287. A pinion gear 291 is mounted on any
convenient support, for example, on a plate extending from the bleeder
flange 113. The pinion gear 291 is arranged for rotation about a
shaft 293 which shaft is in turn supported by the plate 289 and
the pinion gear is positioned so that the teeth thereof engage the
teeth 287 of the rod 281.
As previously noted, and as seen in FIG. 1 the support cone bearing
seat 125 is in direct contact with, and is vertically supported
by, the support cone bearing 129. Further, the bearing 129 is coupled,
with respect to vertical movement, to the mantle 191 through the
clutch housing 131 and the support cone 141. It will therefore be
understood that the vertical location of the rod 281 which is arranged
for linear vertical movement corresponds directly to the vertical
position of the mantle 191. The vertical position of the rod 281
may therefore be used to indicate the crusher setting, that is,
the size to which the cone crusher will reduce material provided
thereto. For the purpose of providing a direct calibrated crusher
setting reading the pinion gear 291 may be coupled in any conventional
manner desired to any conventional reading apparatus. Thus, for
example, the pinion gear 291 might be used to directly drive a needle
type indicator which is calibrated relative to the diameter of the
material processed by the crusher. Alternatively, the rotation of
the pinion gear 291 might be used to drive an intermediate transducer
of any suitable type which would, in turn, provide an indication
of the size of the material discharged by the crusher.
At this time it is appropriate to note that for the rod 281 to
provide correct crusher setting readings it is necessary that the
rod 281 be maintained in an abutting relationship with the bearing
seat 125. It will therefore be understood that it is necessary to
provide a mechanism which will bias or urge the rod 281 upwardly
so that it is maintained in direct contact with the undersurface
of the bearing seat 125. In the embodiment illustrated the biasing
mechanism includes a pair of sealing rings (acting as piston rings)
indicated at 301 and 303 respectively. The lower sealing ring 301
is fixed to the shaft 81 in any conventional manner and the upper
ring 303 is fixed to the rod 281 in any conventional manner. One
or more ports 305 are formed in the wall of the rod 81 thereby permitting
a portion of the lubricating oil flowing through the rod to pass
into the (piston) chamber formed between the rings 301 and 303.
The lubricating oil, which is always flowing into the lubrication
path 83 (the rod 281) under pressure, thus provides an upward force
which acts upon the ring 303 urging it upwardly, thereby urging
the rod 281 upwardly and maintaining the uppermost end of the rod
in abutting contact with the undersurface of the bearing seat 125.
To accommodate the rings 301 and 303 and to provide space for the
vertical movement of the ring 303 a stepped bore, indicated at
307 is provided in the shaft 81. The stepped bore, which has a
diameter greater than the diameter of the remainder of the bore
(the lubrication path 83) of the shaft 81 extends, it will be noted,
only a distance sufficient to accommodate the excursions of the
rod 281. Upward movement of the ring 303 within the stepped bore
will, of course compress any ambient air trapped between the uppermost
portion of the stepped bore and the ring 303. Inasmuch as such compression
of ambient air would cause undesired resistance to the upward movement
of the rod 281 a venting port, indicated at 309 is provided in
the shaft 81. The port 309 which extends into the stepped bore
307 permits air which would otherwise be trapped to escape, thereby
permitting the rod 281 to move upward more easily.
Of course, the rod 281 may be maintained in abutting relationship
with the bearing seat 125 by other, equivalent arrangements, not
shown. For example, the upper portion of the bore of the shaft 81
could be enlarged and the bottom of a spring could be fixedly positioned
at the lower terminus of the enlarged bore. In this arrangement
a collar could be fixedly connected to the rod 281 near the top
portion thereof and the top of the spring could be fixedly connected
to the underside of the collar, thereby compressing the spring between
the lower terminus of the enlarged bore and the collar attached
to the rod 281. The compression force of the spring thus would serve
to urge the rod 281 upwardly. Clearly, selection of a spring having
suitable parameters would be a simple matter of engineering design,
it being understood that such parameters would, in part, be dependent
upon the weight of the rod and the distance between the collar and
the lower terminus of the enlarged bore. It is thus seen that an
arrangement utilizing a spring to maintain the uppermost portion
of the rod 281 in contact with the underside of the support cone
bearing seat 125 which spring arrangement is a viable alternative
for the piston arrangement illustrated, has been described.
Turning now to FIG. 6 the flywheel 148 the uppermost part of
the tubular member 47 a labyrinth seal 150 and the telescoping
labyrinth seal 161 are shown in greater detail. The flywheel 148
which may be made of steel, is bolted (as indicated at 152 in FIG.
1) to the lower portion of the eccentric sleeve 91 and rotates therewith.
To prevent grit, for example, rock dust, from entering into the
interior of the crusher through the space between the rotating flywheel
148 and the stationary member 47 the grease filled labyrinth seal,
indicated at 150 is provided. A grease path 321 which is connected
to a standard grease fitting 323 is formed within the member 47
thus providing a path through which grease may be injected into
the voids of the seal. It is appropriate to note at this point,
because it is most clearly shown in FIG. 6 that the lower sealing
rings 163 are connected by, for example, screws such as the one
indicated at 331 to the flywheel 148. In this manner the required
support for the lower sealing rings 163 of the labyrinth seal 161
may be provided.
Turning now briefly to FIG. 7 the slotted annulus 45 is illustrated
in detail. In particular, it will be noted that the tubular member
69 which forms the housing for the drive shaft 71 is welded to
the walls of the slot, which slot is indicated at 341. In addition,
FIG. 7 clearly illustrates the annular nature of, and the concentric
relationship between, the shaft 81 the hub 41 the hub shoulder
43 and the annulus 45.
OPERATION OF THE CRUSHER
As previously indicated, the function of the crusher is to receive
large pieces of hard material and to reduce the large pieces to
a number of smaller pieces of relatively uniform size. In operation,
chunks of a material such as rock are fed into the feed hopper 1.
The pieces of rock drop into the crushing chamber, which is defined
by the area bounded by the concave 17 and the mantle 191 where
they are then crushed, or compressed, or fractured by striking one
another, resulting in their breakage into smaller pieces. The size
of the pieces passing through the crushing chamber and out of the
crusher unit is determined by the space between the mantle 191 and
the concave 17. This space or distance is in turn controlled, as
previously indicated, by the piston 97. As is clear from FIG. 1
linearly upward movement of the piston 97 causes the mantle 191
to move upward, that is, closer to the concave 17 whereas lowering
the piston 97 causes the mantle 191 to move downward, further from
the stationary concave 17. To effect the vertical movement of the
mantle 191 hydraulic fluid is pumped into, or withdrawn, through
the tubing and coupling combination 99. After the mantle 191 has
been positioned at the vertical level desired, the combination 99
is effectively removed from the system by, for example, closing
a valve (not shown) and the vertical position of the mantle 191
is thus set. As is well known in the art, however, large pieces
of material which are too hard to be crushed (reduced in size) by
the action of the mantle and concave occasionally enter the unit.
It is because of this fact that the accmulator 107 and the gas filled
bag 111 are provided. In the event that a large piece of excessively
hard material (frequently referred to in the art as "tramp
metal") is provided to the crusher, the mantle 191 will obviously
be forced downwardly. The downward movement of the mantle will,
in turn, cause the piston 97 to move downwardly, thereby forcing
some of the hydraulic fluid in the piston chamber 95 and/or the
tubing 101 into the accumulator 107 (it having been noted above
that the combination 99 has been effectively removed from the system).
Because hydraulic fluid is not compressible, while gas is, the increased
pressure on the gas in the bag 111 caused by the increased quantity
of hydraulic fluid in the accumulator 107 will cause the compression
of both the gas bag 111 and the gas therein. After the mantle 191
has been forced downward by the tramp metal a distance sufficient
to permit the tramp metal to pass between the mantle 191 and the
concave 17 (and the metal is passed by the crusher), the compressed
gas in the gas bag 111 expands, forcing hydraulic fluid back into
the chamber 95 and thereby raising the piston 97 to the level at
which it was prior to the entry of the tramp metal into the crushing
chamber.
As just noted, the size of the material passed by the cone crusher
is dependent upon the spacing between the mantle 191 and the concave
17. Clearly, it is desirable to be able to determine, prior to the
operation of the crusher, the size of the pieces which the crusher
will provide. Although the structure of the crusher setting indicator
has already been discussed in detal with regard to FIG. 5 it is
believed appropriate at this time to briefly explain the procedure
involved in calibrating, or "zeroing", the crusher setting
indicator. As is well known in the art, it is relatively easy to
determine the vertical position or height to which the piston 97
has raised the support cone bearing seat 125. The mantle 191 undergoes
continuous wear, however, and thus merely knowing the height to
which the seat 125 has been raised is insufficient to permit an
operator to accurately determine the distance between the mantle
191 and the concave 17. Utilization of the instant crusher setting
indicator, however, permits the operator to raise the piston 97
to its maximum height which is, of course, the height at which the
mantle 191 contacts the concave 17. Under such conditions it is
simple matter for the operator to "zero" a gauge or other
indicator controlled by the pinion gear 291 so as to indicate "zero",
that is, the absence of space between the concave and mantle. The
operator may then lower the piston 97 and the indicator controlled
by the pinion gear will accurately reflect the true vertical distance
between the concave and mantle. In this manner described crusher
setting indicator compensates for mantle and concave wear and accurately
reflects the true spacing therebetween.
As previously noted, the size of the material provided by the crusher
is determined by the distance between the mantle 191 and the concave
17. The reducing action of the crusher is, however, as is well known
in the art, provided by the gyration of the mantle relative to the
concave, the gyration of the mantle having the effect of constantly
increasing and decreasing the space between the mantle and the concave.
The desired gyratory motion of the mantle is here provided for by
the rotation of the drive shaft 71 which causes the eccentric sleeve
91 to rotate about the stationary shaft 81. Because the sleeve 91
has an eccentric configuration, as illustrated and as is conventionally
known in the art, the support cone 141 and the mantle 191 firmly
affixed to the cone 41 will gyrate.
At this point it is appropriate to discuss the operation of the
anti-spin mechanism 225 and it is noted that the structure and operation
of the mechanism is most clearly shown in FIGS. 2 and 2A. As previously
indicated, the mantle 191 gyrates due to the rotation of the eccentric
91. It is well known in the art, however, that the mantle 191 also
rotates as the eccentric 91 rotates notwithstanding the fact that
the bearing surface between the support cone 141 and the eccentric
91 is well lubricated (as will be more fully described below) in
an attempt to reduce friction and wear. In particular, it is well
known that when the crusher is operating in a "no-load"
condition, that is, the eccentric 91 is driven and no material is
being fed to the crusher unit, the mantle 191 tends to rotate in
the same direction as the eccentric 91. It is further known in the
art that when the crusher is in the process of crushing material,
that is, when it is under load, the mantle 191 tends to rotate in
a direction opposite to that in which it rotates when it is not
under load. The design of the internal mechanism of the crusher
unit is, as is conventional in the art, such that mantle rotation
in the "load" direction is permissable while rotation
in the no-load direction is to be avoided because such rotation
can cause extensive wear to the mantle and concave. To prevent mantle
rotation in the no-load direction the anti-spin mechanism 225 is
utilized. In particular, the anti-spin mechanism is arranged so
that the mantle 191 may rotate in the load direction but will be
prevented (within limits which are more fully discussed below) from
rotating in the no-load direction.
Referring now to FIGS. 2 and 2A, it will be understood that when
the crusher is under load the motor 231 is caused to rotate in the
"load" direction by the rotation of the clutch housing
131 which is fixedly connected to the support cone 141. The rotation
of the motor 231 in the load direction causes the lubricating fluid
within the reservoir 241 to be drawn upwardly through the check
valve 245 and the fluid is returned to the reservoir through the
manifold 243 and the tubing 249. However, when the motor 231 is
caused to rotate in the no-load direction the lubricating fluid
is drawn into the manifold 243 through the tubing 249. The fluid
cannot, however, be returned to the reservoir chamber through the
check valve 245 because it is a unidirectional valve. Furthermore
the fluid cannot be returned to the reservoir chamber through the
ball-type relief valve 247 because the valve 247 is biased closed
by the action of a conventional spring loaded mechanism, not shown.
In this manner the motor 231 is prevented from rotating in the no-load
direction and the mantle 191 is therefore also barred from rotating
in the no-load direction. In the event, however, that the mantle
191 is urged to rotate in the no-load direction with sufficient
force (urging the motor housing 231 to rotate in such direction
as well) then, rather than risk the possible breakage of components
of the crusher, the motor 231 is permitted to rotate in the no-load
direction, thereby permitting the mantle 191 to also rotate in the
otherwise undesired direction. To accomplish this end the spring
maintaining the relief valve 247 in a closed condition is so selected
as to permit the lubricating fluid to open the valve 247 when the
fluid pressure applied to the spring is sufficient to overcome the
counter-acting spring force, thereby permitting the fluid to return
to the reservoir and the motor and mantle to rotate. It will further
be understood that the just described anti-spin mechanism is self-resetting.
Thus when the mantle 191 has been forced to rotate in the no-load
direction (the relief valve 247 has opened) and the force applied
to the mantle 191 is subsequently reduced to a level below that
necessary to overcome the countervailing spring force of the valve,
the spring will again close the valve, once again preventing the
rotation of the mantle 191 in the no-load direction.
Turning now briefly to a discussion of the lubrication system of
the crusher, it is first noted that many portions of the system
have already been discussed. Thus, for example the lubricating paths
83 and 127 the fact that the lubricating fluid fills the chamber
within the clutch housing 131 and within the reservoir 241 and
the fact that the same lubricating fluid may be utilized to urge
the crusher setting indicator rod 281 upward, have already been
discussed. Nevertheless, it is believed appropriate at this point
to briefly note the major features of the system. Initially, it
is appropriate to indicate that the lubricating fluid is not merely
injected into the crusher system where it remains inactive but,
rather, that the overall lubrication system, some portions of which
are not illustrated, is a constantly circulating system. As a starting
point, it may be noted that lubricating fluid flows into the lubrication
paths 83 via the fitting 283. The lubricating fluid also passes
through the ports 85 and thus between the eccentric 91 and the shaft
81. In addition, the lubricating fluid fills the chamber bounded
by the lower portion of seat 125 the upper portion of the shaft
81 and the radially inner portion of the eccentric 91. The lubricating
fluid is further conducted along the path indicated at 127 and coats
the bearing surface between the support cone bearing 129 and the
support cone bearing seat 125. Clearly, therefore, the fluid also
fills the chamber radially outward of the bearing 129 and the seat
125. In addition, the lubricating fluid fills the chamber within
the clutch housing 131 and, as noted above, it fills the anti-spin
mechanism reservoir 241. Additionally, the lubricating fluid flows
into the chamber bounded by the radially outward portion of the
hub 41 the lower portion of the bevel gear drive assembly 73 and
the upper portion of the shaft housing member 69. The lubricating
fluid is conducted from the last described chamber through a drain
coupling 365 (most clearly seen in FIG. 3) by a pump (not shown)
and through a filtration system (not shown) from which it may be
returned to the crusher via the fitting 283. It is thus seen that
the lubrication system of the instant crusher insures a constantly
circulating supply of clean lubricating fluid.
It will be understood that the foregoing description of the preferred
embodiment of the present invention is for purposes of illustration
only and that the various structural and operational features as
herein disclosed are susceptible to a number of modifications and
changes none of which entail any departure from the spirit and scope
of the present invention as defined in the hereto appended claims. |