CA1147318A - Fabricated cone crusher - Google Patents
Fabricated cone crusherInfo
- Publication number
- CA1147318A CA1147318A CA000399584A CA399584A CA1147318A CA 1147318 A CA1147318 A CA 1147318A CA 000399584 A CA000399584 A CA 000399584A CA 399584 A CA399584 A CA 399584A CA 1147318 A CA1147318 A CA 1147318A
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- Canada
- Prior art keywords
- crusher
- mantle
- rod
- cone
- setting indicator
- Prior art date
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Abstract
FABRICATED CONE CRUSHER
Abstract of the Disclosure 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 struct-ure, 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 movable 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.
This abstract is not to be taken either as a complete exposi-tion or as a limitation of the present invention, the full nature and extent of the invention being discernable only by reference to an from the entire disclosure.
Abstract of the Disclosure 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 struct-ure, 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 movable 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.
This abstract is not to be taken either as a complete exposi-tion or as a limitation of the present invention, the full nature and extent of the invention being discernable only by reference to an from the entire disclosure.
Description
~473~8 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-spin mechanisms and crusher settillg indicators.
This is a division of copending Canadian Patent Application Serial No. 335,731, filed 5eptember 17, 1979.
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 presen-tly widely use~ in the con-crete and aggregate industry have numerous character-istics which make them less than ideal. For example, such crushers must have extra-ordinarily 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 Erames h~ve generally proved to be of su~ficient strength, the cost of their manu-facture is quite high and they are -therefore, from an economic point of view, less than completely satis~
factory. In an effort to overcome this negative aspect it has been proposed to fabrica-te the lower portion of the main frame of such a crusher from pre--formed com-ponents rather than to cast it and to thereby obtain substantial savings. ~n example of such a cone crusher -- 1 -- ' mab/
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which includes a fabricated lower main frame porti.on is provided in U.S. Patent No. 3,150,839. It is noted, however, that even this patent teaches a crusher main frame structure which inc].udes cast members, in par-ticular, this pa-tent teaches a structure uti.lizing a cast center hub. The industry, recognizing the ad-vanta~es of fabricated main frames for crushers has attempted - ~47318 to provide main fxame structures which axe completely fa~ricated, 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. Patent No. 3,843, 068 which is fabricated solely from pre-Eormed components which are welded together. Such structures, although providing definite ad~an~ages..over the earlier cast structures are nevertheless not completely satisfactory in that they frequently require great numbers of components to fulfi~l:. their function. For example, io the last notëd patent includes an adapter plate for permitting the mating of the center hub with the countershaft which houses the L~e~uired 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 d 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 ~agnitude 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 regàrding the size of the material to be provided by the crusher with a desirea degree of accuracy. It is, of course, possible to accurately and inexpensively determine the crusher setting by pc//~)" - 3 -~ 7~
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 o the crusher.
Cone crushers of the type here under discussion include a gyratory member yenerally 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 ~ot in the process of crushing mat'erial.' Further, the mantle tends to rotate in a second direction, opposite to the flrst 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 fre~uently are in the form o devlces whlch absolutely bar the rotation of the mantle in the first direction ~hile permitting the mantle ~o freely rotate in the second airection. The utility of such~mechanisms has provéd to be less than completely satisfactory because absolutely barring the rotation of the mantle in ~he first direction, may, under conditions where ~he 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 i5 therefore an important object of`the present invention to provide an improved cone crusher structure by means of which the aor~said drawbacks and disadvantages may be most efficaciously avoided.
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~473~8 It is an object of this invention to provide a fabricated frame for a cone crusher which can be manu-factured at a minimum cost.
It is another importan-t 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 still another object of the instant in-vention to provide a crusher setting indicator for a cone crusher structure which is mechanically simple and in-expensive.
It is yet another object of the instant invention to provide a crusher settlng indicator for a cone crusher which is more accurate than presently known indicators.
According to the instant invention there is provided a crusher setting indioator for a cone crusher, whioh crusher includes a moveable man-tle 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 re-lated to the position of the mantle along the line, and means responsive to the position of the rod along the line for providing an indicat1on o 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:
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BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a cross-sectional plan view of the cone crusher of the instant inventioni 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. l;
Fig. 3 is a plan view taken along lines 3-3 of Fig. l;
Fig. 4 is a cross-sectional plan view taken along lines 4-4 of Fig. l;
Fig. 5 is a detailed cross-sectional plan view of the crusher setting indicator of the instant in-vention;
Fig. 6 is a detailed cross-sectional plan view of the sealing arrangement of the ins-tant cone crusher; and Fig. 7 is a cross-sectional plan vicw taken along lines 7-7 of Fig. 1.
DESCRIPTION OF THE PREFERRED EMBODI~ENT
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 fram~ portion, there is illustrated mab/
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a feed hopper (although feed hoppers are generally considered hy 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 l which includes a.fabricated tub~lar member 3j which member may be fabricated.from bend rolled steel plateO A fabricated member 5, which has the.general cross-sectional configuration of a trùncated cone and a fabricated member.7 which also has the general cross-sectional.configuration of a truncated cone are both welded 9 at their upper peripheries, to the member 3. The members 5 and 7 are also welded to onè another along their contiguous lengths, it being noted that the member 5 is lonser than the member 7. A fabricated tubular member 9 is weldea at its upper periphery to the lower periphery of the truncated member 5 and to the.side.of the mem~er.7. 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 ll is formed with a plurality of holes therein and it is thereby adap$ed t~ be irmly affixed to an annulus 13 t which is formed with a plurality of countersunk threaded holes., by any conventional means, for example, by screws such as the one indicated at 15.
An upper crushing member or concave 17 having the general cross-sectional configuration of a truncated cone is cast from an extremely hard and long wearing material such as/ for example, manganese steel, and it is formed wi$h a plurality of gripping or hook members, one of which is indicated at 19. The concave-17 is ~ain~a-mé~:in~posi$io~ ~y a plur~lity of gripping m~mbers 21 which pass ~hrough apertures 20 form~d in the annulus 13, which gripping me~bers.21 may have any desired configuration. In the embodiment ~ 7 -pC/ ! ', 733~
. 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 draw.ing the concave i7 upwardly to îts 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.spacea circumferentially. and there may be, for example, 16 such ribs spaced 22.5 apart, as clearly seen in Fig.
4. A plurali~y of the ri~s 25 are formed with apertures 27 there-through so as to facilitate the lifting of the upper portion of the fabricated main frame o the crusXer 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 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 indica~e~ at 33 are formed .
at various locations about the periphery of the tubular member 29 which apertures may be blocked by, for example, h~nged doors such as th.e one indicated at 35 so that access may be had to the inter-ior 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 ~ - 8 -pC/-~,7 7;~18 of the upper main frame portion of the crusher. The ribs 30, which have "U" shaped cross-sectional conEigur-ations (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 oE 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. ~ 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, t'ne member 29 and the liner 31 into a rigid structure. A horizontal an-nulus 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 por-ti.on will be described in detail below.
The above-described upper frame is also des--- g _ mab/
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cribed and is claimed in above-ldentified parent ap-plication Serial No. 335,731.
Turning now to a description of the lower main frame portion and referring to Fig. 1, it is seen that the lower main frame por-tion includes a forged steel center hub 41 which has an annular shoulder 43 formed at the uppe~ 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 fabricàted tubular member 47, which may be, for example, of bend rolled steel piate, is welded to the annulus 45 at the outer periphery thereof An annulus 49, ori.ented to extend orthogonally relative to the member 47 is welded thereto interjacent the ends thereof. The annulus 49 is formed with a plurality of aperatures 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 lndicated at 53 thereby accomplishing the connection of the upper and lower main frame portions.
~ plurality of ribs or gussets 61, for example, three (most c].early seen ln 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 . -- 10 --mab/ ' , 3~8 ..
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.
The above~described lower main frame is des~
cribed and is also claimed in copending Canadian divi~
sional application Serial No. 399,583, filed March 26, 1982.
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 aper-ture 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, a1ternat~ly, the annuk~ 45 ~ay ~riq~na11y b- form-d - a :
p~ - 11 -mab/ ~--~. ' "~ 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..l shows the drive shaft 71.driving the cone crusher by means of a conventiona1 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 F~g. 3), are welded to the center hu~ 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 4~ as do the ribs 61, the xibs 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.
Add1$ional 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 ~2. 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 slee~e 91, which is dri~en by ~ - 12 -pc/
~473~L8 the drive shafk 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 kurn 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 shaEt 81 and the eccentric 91, a bearing of relatively so~t alloy metal may be positioned.between the adjacent bearing surfaces of the shaft 81 and the eccentric 91.. Alternatively, a layer of relati~ely 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 piskon 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 ~ubing and coupling combination, generally indicated at 99, to a section o~ conventional tubing indicated ak 101. The tubing 101, together with aconventional 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 ~onnectea to an accumulatox 107. The accumulakor 107 is supported by a frame, indicated generally at 108. The frame~08~is attached to the lower portion of the main frame by any conventional means such as, for example, a clamp indicaked 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 inkerior 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 with;n the chamber 95 from exiting through the bottom of the shaft pc/~ 13 -~7~
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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. ~he 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 afixed 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.l41 which support cone is supported by a circular shoulder 142 ormed 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 th.e 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 indicatea at 152 and the fly-wheel 148 is arranged to rotate with the eccentric 91. Connected between the support cone 141 and the flywheel 148 is a ~rease fllled labyrinth seal indicated generally at 161, the purpose of pc/, ~J
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which is to prevent grit such as particles of 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 pluarlity 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 rrusher 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
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wear collar 181, which collar may be made of low carbon steel, is welded to the support cone 1~1, 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 whichhas 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 X,;
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195 is a feed plate lg7 which may be made of low carbon steel.
The plate l9i 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 ~xternally threaded,clutch housing 131 forcing the collar 193 downwardly and.thereby urging the mantle l91,into'.snug engagement with the support cone 141. To increase the downward force applied ,by the collar 193 to the mantle.l91, 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 asinternally~, until the nut 205 is snug against the collar.l93., 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 screwsr such as the one pC/' ! - 16 -~47318 . .
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, i5 a shat 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 a 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 ~he lubricating oil filled reservoir 241 are a manifold 243, a check valve 245, ana a relief valve 247, each of ~hich 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 reservoir 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.
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~731~3 -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 upparmost and the manifold being positioned at.the bottom of the reservoir chamber, would .
clearly provide an e~uivalent structure. The shaft of the motor 231 which is, as previously noted, coupled to the shaft' 221 by means of the universal joint 22.3 does.not rotate. Rather, the motor 231 is arranged for rotationO 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 o the clutch housing, the support cone 141 and t~e mantle 191 will be ' .: ! ' directly related to the rotation o-E the motor 231. Alternatively, however, it may be desired to attach the' motox 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 loca-ted with-in 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 portionj indicated at 2851 extends into a lubrication fitting 283 located just below the lowermost portion of the lubrication path 83. It is appropriate to pc/~
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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 f1ange 113.. The'pinion gear 291 is arranged for rotation about.a sXaft 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 conta~t wi'th, and is vertically supported by, the support cone bearing 129. Further, the bearing 129 is coupled, with respect to vertical movement, to the mantle l91r through the clutch housing 131 and the support cone 141. It will therefore be understood that the ~ertical location of the rod 281, : which is arranged for linear vertical movement corresponds directly to the vertical position of the mantle 191. The ~ertical position o~ 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 provid1ng 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 t.ype 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~
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At this time it is appropriate to note that for the rod 281 to provide correct crusher setting xeadings 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 neces~ary to provide a mechanism.which will bias or urge the rod 281 upwardly so that it is maintained in direct contact with the under-surface'of the beariny 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 ormed in the wall of the rod 81 thereby permitting a portion of the lubricating oil flowing through the roa' to pass into the (piston) chamber f.ormed between the rings 301. and 303. The lubricating oil, which is always flowing into the .: ; . .
lubrication path 83 (the ~od 281~ under pressure, thus provides an upward orce which acts upon.the ring 303 urging it upwardly, thereby urg.ing.the rod 281 upwardly and maintaining the uppermost end of the rod in abutting contact with th.e. undersurface of the bearing seat .' 125. To accommodate the rlngs 301 and 303 and to provide space for the vertical movement of the ring 303, a stepped bore~ indicated at 3Q7, is provided in the shaft 81. The stepped hore, 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 w;ll, of course cornpress any ambient air trapped between the uppermos~
portion of the stepped boreand"~he-ring 303. Inasmuch as su~h compression-of ambient air would cause undesired resistance to the upward move~en~ of the pC/7j ' ' rod 281, a venting port, indicated at 309, is provided in the shaft 81. The pork 309, which extends into the stepped bore 307, permits air which would otherwise be trapped to escape, thereby permitting the rod 281 to move up~ard more easily.
Of course, the rod 281 may he 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 boreO 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 para-meters 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 alternati~e 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 ~ - 21 -pC~
~14L'731&~
into the interior of the crusher through the space between the rotating flywheel 148 and the stationary m~mber 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, ~ecause it is most cleaxl~ 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 siotted annulus 45 is illustrated in detail. In particular, it will ~e noted that the tubula~ member 69, which..forms the housing foL 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 na~ure of, and the concentric relationship between, the shaft 81, the hub 41, the hub shoulder 43 and the annulus-45.
. OPER~TION OF TH~ ~RUSHER
: 20 . 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 crushin~ 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 i.n their breakage into smaller pieces. The size of the pieces passing-through the crushing cha~ber and out of the crusher unit is determined by the space between the m~ntle 191 and ~he concave 17. This space or distance pc/~ 22 -~73~
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 ~7 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 le~el desired, the combination 99 is effectively removed from ~he 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 accumulator 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 downwar~ movement of $he . mantle will, in turn, cause the piston.97 to move downwardly,thereby forcing.some of the hydraulic 1uid in the piston chamber ~5 and/or the tubing 101 into the accumulator 107, (it having been noted above that the.combination 99 ~as 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 b.~ the tramp metal a ~istance . .
sufflcient to permit the tramp metal to pass between the mantle 191 and the concave 17 (and ~hel~tal is passed hy the crusher), the compressed gas in the gas ~y .
pc~ 23 -'73~
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 çrusher will.provide. Although the structure of the crusher setting indicator has already been discussed in detail with xegard to Fig-O 5,.it is believed appropriate at this time to briefly explain the procedure involYed.in calibrating, or "zeroing", the crusher setting indicator. ~s 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 1~5.
The mantle 191 undergoes continuous wear, however, and thus mere.ly .
knowing the height to which the seat 125 has been raised is in-sufficient to permit an operator to accurately determine the dis~ance 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 whi.ch is, of course, th~
height at which the mantle 191 contacts the concave 17. Under such conditions it is a simple matter for the operator to "zero" a gauge or other indicator controlled by the pinion qear 291 so as to indicate "zero", that: is, the absence of space between the concave and mantle. The operator may then iower 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 l~ner.the descr~bed crusher setting indicator a~nsates for mantle and concave wear and accurately reflects the true spacing therebebween.
- 24 _ pc~
3~b~
As previously noted, the size of the material provided by the crusher i5 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.~y the rotation of the drive-shaft 71 which causes the eccentric sleeve 91 to rotate about the stationary shaft 81. Because the sleeve gl has an eccentric conf.iguration, as. illustrated and as is conventionally known in the art, the sup~ort 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 no~with-standing 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, lt 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 191. It is further kno~n 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 ~ - 25 -pC/~ J
:
~7318 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 $he mantle 191 may rotate in the Ioad direction but will be prevented twithin limits which are more fuIly discussed below) from rotating in the no-load direction.
~o Re~erring now to Figures 2 and 2A, it will be understood -that when the crusher is under load the motor 231 is caused torotate în the "load" direction by the rotation o the clutch housing 131 which is fixedly connected to the support cone 141. The xotation of the motor 231 in the load direction causes the lubricating fluid . ~ . . .
within the reservoir 241 to be drawn upwardly through the check valve 225 and the fluid is returned to the reservoir through the manifold 243 and the tu~ing 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 retuxned to the reservoir chamber through the check valve 245 because it is a unidirectional valve.~ Furthermore, the f1uid cannot be returned to the reservolr 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 mannex 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 rctate in the no-load direction with sufficient force (urgin~ the motor housing 231 to rotate in such direction as well) then, rather than risk the possible ~ - 26 -PC/~
~4~318 c 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 other-wise undesired direc-tion. To accomplish this end the spring maintaining the relief valve 247 in a closed con-dition 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 s~ring 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 sel~-resetting. Thus when the mantle 191 has been forced to rotate in the no-load directlon (the reliçf valve 247 has opened) and the force applied to the mantle 191 is subsequently re-duced to a level below that necessary to overcome the countervailing spring force of the valve, the spri~g will again close the valve, once again preventing the rotation of the mantle 191 in the no-load direction.
The above-described anti-spin mechanism is also described and is also claimed in a copending Canadian Divisional application Serial No. 399,585, ~iled March 26, 198~.
Turning now briefly to a discussion o~ 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 mab/,~
~731~
the clutch housing 131 and within the reservoir 241, and the fact that the same lubricating fluid may be utilized to urge the crusher se-tting indicator rod 281 upward, have already been discussed. Nevertheless, it is believed appropriate at thi.s po.i.nt 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 reamins inactive but, rather, -that the overall lubrication system, some portions oE which are not il lus tra ted, i s a ~ ons tantly i rcu: atln-l sys tem .
.~
~, - 2~ -mab/
' ~4'731~
:
As a starting point, it may be noted $hat 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 ~nd the radially inner portion of the eccentric 91. The lubricating fluid is further conducted along the path indica~ed at.l27 and coats the bearing surface between the support cone bearing 129 and the support cone bearing seat 125.
1~ 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 41f the lower portion.of the bevel gear drive assembly 73 and the upper portion.of the shat 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 fil-tration 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 c.irculating supply of clean lubricating flui~.
It will be understood that the foregoing description of the preferred e~bodiment of the present invention is for purposes of illustration only and that ~he various structural and operational featwres as herein disclosed.are susceptible to a number of modif ications and changes none of whi~h.entail any departure from the spirit and SCOp2 of the present invention as defined in the hereto appended claims~
~ - 29 -pc/,~
This is a division of copending Canadian Patent Application Serial No. 335,731, filed 5eptember 17, 1979.
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 presen-tly widely use~ in the con-crete and aggregate industry have numerous character-istics which make them less than ideal. For example, such crushers must have extra-ordinarily 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 Erames h~ve generally proved to be of su~ficient strength, the cost of their manu-facture is quite high and they are -therefore, from an economic point of view, less than completely satis~
factory. In an effort to overcome this negative aspect it has been proposed to fabrica-te the lower portion of the main frame of such a crusher from pre--formed com-ponents rather than to cast it and to thereby obtain substantial savings. ~n example of such a cone crusher -- 1 -- ' mab/
31~
which includes a fabricated lower main frame porti.on is provided in U.S. Patent No. 3,150,839. It is noted, however, that even this patent teaches a crusher main frame structure which inc].udes cast members, in par-ticular, this pa-tent teaches a structure uti.lizing a cast center hub. The industry, recognizing the ad-vanta~es of fabricated main frames for crushers has attempted - ~47318 to provide main fxame structures which axe completely fa~ricated, 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. Patent No. 3,843, 068 which is fabricated solely from pre-Eormed components which are welded together. Such structures, although providing definite ad~an~ages..over the earlier cast structures are nevertheless not completely satisfactory in that they frequently require great numbers of components to fulfi~l:. their function. For example, io the last notëd patent includes an adapter plate for permitting the mating of the center hub with the countershaft which houses the L~e~uired 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 d 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 ~agnitude 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 regàrding the size of the material to be provided by the crusher with a desirea degree of accuracy. It is, of course, possible to accurately and inexpensively determine the crusher setting by pc//~)" - 3 -~ 7~
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 o the crusher.
Cone crushers of the type here under discussion include a gyratory member yenerally 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 ~ot in the process of crushing mat'erial.' Further, the mantle tends to rotate in a second direction, opposite to the flrst 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 fre~uently are in the form o devlces whlch absolutely bar the rotation of the mantle in the first direction ~hile permitting the mantle ~o freely rotate in the second airection. The utility of such~mechanisms has provéd to be less than completely satisfactory because absolutely barring the rotation of the mantle in ~he first direction, may, under conditions where ~he 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 i5 therefore an important object of`the present invention to provide an improved cone crusher structure by means of which the aor~said drawbacks and disadvantages may be most efficaciously avoided.
pc/,~ 4 -.
~473~8 It is an object of this invention to provide a fabricated frame for a cone crusher which can be manu-factured at a minimum cost.
It is another importan-t 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 still another object of the instant in-vention to provide a crusher setting indicator for a cone crusher structure which is mechanically simple and in-expensive.
It is yet another object of the instant invention to provide a crusher settlng indicator for a cone crusher which is more accurate than presently known indicators.
According to the instant invention there is provided a crusher setting indioator for a cone crusher, whioh crusher includes a moveable man-tle 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 re-lated to the position of the mantle along the line, and means responsive to the position of the rod along the line for providing an indicat1on o 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:
mab/
, ~.
~ ' :
3~
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a cross-sectional plan view of the cone crusher of the instant inventioni 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. l;
Fig. 3 is a plan view taken along lines 3-3 of Fig. l;
Fig. 4 is a cross-sectional plan view taken along lines 4-4 of Fig. l;
Fig. 5 is a detailed cross-sectional plan view of the crusher setting indicator of the instant in-vention;
Fig. 6 is a detailed cross-sectional plan view of the sealing arrangement of the ins-tant cone crusher; and Fig. 7 is a cross-sectional plan vicw taken along lines 7-7 of Fig. 1.
DESCRIPTION OF THE PREFERRED EMBODI~ENT
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 fram~ portion, there is illustrated mab/
~' `'.
31~
a feed hopper (although feed hoppers are generally considered hy 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 l which includes a.fabricated tub~lar member 3j which member may be fabricated.from bend rolled steel plateO A fabricated member 5, which has the.general cross-sectional configuration of a trùncated cone and a fabricated member.7 which also has the general cross-sectional.configuration of a truncated cone are both welded 9 at their upper peripheries, to the member 3. The members 5 and 7 are also welded to onè another along their contiguous lengths, it being noted that the member 5 is lonser than the member 7. A fabricated tubular member 9 is weldea at its upper periphery to the lower periphery of the truncated member 5 and to the.side.of the mem~er.7. 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 ll is formed with a plurality of holes therein and it is thereby adap$ed t~ be irmly affixed to an annulus 13 t 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 wi$h a plurality of gripping or hook members, one of which is indicated at 19. The concave-17 is ~ain~a-mé~:in~posi$io~ ~y a plur~lity of gripping m~mbers 21 which pass ~hrough apertures 20 form~d in the annulus 13, which gripping me~bers.21 may have any desired configuration. In the embodiment ~ 7 -pC/ ! ', 733~
. 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 draw.ing the concave i7 upwardly to îts 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.spacea circumferentially. and there may be, for example, 16 such ribs spaced 22.5 apart, as clearly seen in Fig.
4. A plurali~y of the ri~s 25 are formed with apertures 27 there-through so as to facilitate the lifting of the upper portion of the fabricated main frame o the crusXer 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 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 indica~e~ at 33 are formed .
at various locations about the periphery of the tubular member 29 which apertures may be blocked by, for example, h~nged doors such as th.e one indicated at 35 so that access may be had to the inter-ior 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 ~ - 8 -pC/-~,7 7;~18 of the upper main frame portion of the crusher. The ribs 30, which have "U" shaped cross-sectional conEigur-ations (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 oE 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. ~ 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, t'ne member 29 and the liner 31 into a rigid structure. A horizontal an-nulus 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 por-ti.on will be described in detail below.
The above-described upper frame is also des--- g _ mab/
`~
73~
cribed and is claimed in above-ldentified parent ap-plication Serial No. 335,731.
Turning now to a description of the lower main frame portion and referring to Fig. 1, it is seen that the lower main frame por-tion includes a forged steel center hub 41 which has an annular shoulder 43 formed at the uppe~ 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 fabricàted tubular member 47, which may be, for example, of bend rolled steel piate, is welded to the annulus 45 at the outer periphery thereof An annulus 49, ori.ented to extend orthogonally relative to the member 47 is welded thereto interjacent the ends thereof. The annulus 49 is formed with a plurality of aperatures 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 lndicated at 53 thereby accomplishing the connection of the upper and lower main frame portions.
~ plurality of ribs or gussets 61, for example, three (most c].early seen ln 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 . -- 10 --mab/ ' , 3~8 ..
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.
The above~described lower main frame is des~
cribed and is also claimed in copending Canadian divi~
sional application Serial No. 399,583, filed March 26, 1982.
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 aper-ture 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, a1ternat~ly, the annuk~ 45 ~ay ~riq~na11y b- form-d - a :
p~ - 11 -mab/ ~--~. ' "~ 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..l shows the drive shaft 71.driving the cone crusher by means of a conventiona1 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 F~g. 3), are welded to the center hu~ 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 4~ as do the ribs 61, the xibs 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.
Add1$ional 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 ~2. 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 slee~e 91, which is dri~en by ~ - 12 -pc/
~473~L8 the drive shafk 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 kurn 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 shaEt 81 and the eccentric 91, a bearing of relatively so~t alloy metal may be positioned.between the adjacent bearing surfaces of the shaft 81 and the eccentric 91.. Alternatively, a layer of relati~ely 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 piskon 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 ~ubing and coupling combination, generally indicated at 99, to a section o~ conventional tubing indicated ak 101. The tubing 101, together with aconventional 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 ~onnectea to an accumulatox 107. The accumulakor 107 is supported by a frame, indicated generally at 108. The frame~08~is attached to the lower portion of the main frame by any conventional means such as, for example, a clamp indicaked 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 inkerior 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 with;n the chamber 95 from exiting through the bottom of the shaft pc/~ 13 -~7~
:
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. ~he 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 afixed 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.l41 which support cone is supported by a circular shoulder 142 ormed 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 th.e 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 indicatea at 152 and the fly-wheel 148 is arranged to rotate with the eccentric 91. Connected between the support cone 141 and the flywheel 148 is a ~rease fllled labyrinth seal indicated generally at 161, the purpose of pc/, ~J
3:~
which is to prevent grit such as particles of 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 pluarlity 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 rrusher 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 1~1, 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 whichhas 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 X,;
pc/, 73~
.
195 is a feed plate lg7 which may be made of low carbon steel.
The plate l9i 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 ~xternally threaded,clutch housing 131 forcing the collar 193 downwardly and.thereby urging the mantle l91,into'.snug engagement with the support cone 141. To increase the downward force applied ,by the collar 193 to the mantle.l91, 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 asinternally~, until the nut 205 is snug against the collar.l93., 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 screwsr such as the one pC/' ! - 16 -~47318 . .
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, i5 a shat 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 a 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 ~he lubricating oil filled reservoir 241 are a manifold 243, a check valve 245, ana a relief valve 247, each of ~hich 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 reservoir 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.
~ - 17 -pc/-~ ~
~731~3 -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 upparmost and the manifold being positioned at.the bottom of the reservoir chamber, would .
clearly provide an e~uivalent structure. The shaft of the motor 231 which is, as previously noted, coupled to the shaft' 221 by means of the universal joint 22.3 does.not rotate. Rather, the motor 231 is arranged for rotationO 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 o the clutch housing, the support cone 141 and t~e mantle 191 will be ' .: ! ' directly related to the rotation o-E the motor 231. Alternatively, however, it may be desired to attach the' motox 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 loca-ted with-in 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 portionj indicated at 2851 extends into a lubrication fitting 283 located just below the lowermost portion of the lubrication path 83. It is appropriate to pc/~
3L1~73~
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 f1ange 113.. The'pinion gear 291 is arranged for rotation about.a sXaft 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 conta~t wi'th, and is vertically supported by, the support cone bearing 129. Further, the bearing 129 is coupled, with respect to vertical movement, to the mantle l91r through the clutch housing 131 and the support cone 141. It will therefore be understood that the ~ertical location of the rod 281, : which is arranged for linear vertical movement corresponds directly to the vertical position of the mantle 191. The ~ertical position o~ 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 provid1ng 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 t.ype 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~
pc/,~
L73~
At this time it is appropriate to note that for the rod 281 to provide correct crusher setting xeadings 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 neces~ary to provide a mechanism.which will bias or urge the rod 281 upwardly so that it is maintained in direct contact with the under-surface'of the beariny 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 ormed in the wall of the rod 81 thereby permitting a portion of the lubricating oil flowing through the roa' to pass into the (piston) chamber f.ormed between the rings 301. and 303. The lubricating oil, which is always flowing into the .: ; . .
lubrication path 83 (the ~od 281~ under pressure, thus provides an upward orce which acts upon.the ring 303 urging it upwardly, thereby urg.ing.the rod 281 upwardly and maintaining the uppermost end of the rod in abutting contact with th.e. undersurface of the bearing seat .' 125. To accommodate the rlngs 301 and 303 and to provide space for the vertical movement of the ring 303, a stepped bore~ indicated at 3Q7, is provided in the shaft 81. The stepped hore, 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 w;ll, of course cornpress any ambient air trapped between the uppermos~
portion of the stepped boreand"~he-ring 303. Inasmuch as su~h compression-of ambient air would cause undesired resistance to the upward move~en~ of the pC/7j ' ' rod 281, a venting port, indicated at 309, is provided in the shaft 81. The pork 309, which extends into the stepped bore 307, permits air which would otherwise be trapped to escape, thereby permitting the rod 281 to move up~ard more easily.
Of course, the rod 281 may he 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 boreO 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 para-meters 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 alternati~e 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 ~ - 21 -pC~
~14L'731&~
into the interior of the crusher through the space between the rotating flywheel 148 and the stationary m~mber 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, ~ecause it is most cleaxl~ 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 siotted annulus 45 is illustrated in detail. In particular, it will ~e noted that the tubula~ member 69, which..forms the housing foL 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 na~ure of, and the concentric relationship between, the shaft 81, the hub 41, the hub shoulder 43 and the annulus-45.
. OPER~TION OF TH~ ~RUSHER
: 20 . 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 crushin~ 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 i.n their breakage into smaller pieces. The size of the pieces passing-through the crushing cha~ber and out of the crusher unit is determined by the space between the m~ntle 191 and ~he concave 17. This space or distance pc/~ 22 -~73~
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 ~7 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 le~el desired, the combination 99 is effectively removed from ~he 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 accumulator 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 downwar~ movement of $he . mantle will, in turn, cause the piston.97 to move downwardly,thereby forcing.some of the hydraulic 1uid in the piston chamber ~5 and/or the tubing 101 into the accumulator 107, (it having been noted above that the.combination 99 ~as 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 b.~ the tramp metal a ~istance . .
sufflcient to permit the tramp metal to pass between the mantle 191 and the concave 17 (and ~hel~tal is passed hy the crusher), the compressed gas in the gas ~y .
pc~ 23 -'73~
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 çrusher will.provide. Although the structure of the crusher setting indicator has already been discussed in detail with xegard to Fig-O 5,.it is believed appropriate at this time to briefly explain the procedure involYed.in calibrating, or "zeroing", the crusher setting indicator. ~s 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 1~5.
The mantle 191 undergoes continuous wear, however, and thus mere.ly .
knowing the height to which the seat 125 has been raised is in-sufficient to permit an operator to accurately determine the dis~ance 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 whi.ch is, of course, th~
height at which the mantle 191 contacts the concave 17. Under such conditions it is a simple matter for the operator to "zero" a gauge or other indicator controlled by the pinion qear 291 so as to indicate "zero", that: is, the absence of space between the concave and mantle. The operator may then iower 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 l~ner.the descr~bed crusher setting indicator a~nsates for mantle and concave wear and accurately reflects the true spacing therebebween.
- 24 _ pc~
3~b~
As previously noted, the size of the material provided by the crusher i5 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.~y the rotation of the drive-shaft 71 which causes the eccentric sleeve 91 to rotate about the stationary shaft 81. Because the sleeve gl has an eccentric conf.iguration, as. illustrated and as is conventionally known in the art, the sup~ort 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 no~with-standing 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, lt 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 191. It is further kno~n 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 ~ - 25 -pC/~ J
:
~7318 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 $he mantle 191 may rotate in the Ioad direction but will be prevented twithin limits which are more fuIly discussed below) from rotating in the no-load direction.
~o Re~erring now to Figures 2 and 2A, it will be understood -that when the crusher is under load the motor 231 is caused torotate în the "load" direction by the rotation o the clutch housing 131 which is fixedly connected to the support cone 141. The xotation of the motor 231 in the load direction causes the lubricating fluid . ~ . . .
within the reservoir 241 to be drawn upwardly through the check valve 225 and the fluid is returned to the reservoir through the manifold 243 and the tu~ing 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 retuxned to the reservoir chamber through the check valve 245 because it is a unidirectional valve.~ Furthermore, the f1uid cannot be returned to the reservolr 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 mannex 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 rctate in the no-load direction with sufficient force (urgin~ the motor housing 231 to rotate in such direction as well) then, rather than risk the possible ~ - 26 -PC/~
~4~318 c 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 other-wise undesired direc-tion. To accomplish this end the spring maintaining the relief valve 247 in a closed con-dition 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 s~ring 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 sel~-resetting. Thus when the mantle 191 has been forced to rotate in the no-load directlon (the reliçf valve 247 has opened) and the force applied to the mantle 191 is subsequently re-duced to a level below that necessary to overcome the countervailing spring force of the valve, the spri~g will again close the valve, once again preventing the rotation of the mantle 191 in the no-load direction.
The above-described anti-spin mechanism is also described and is also claimed in a copending Canadian Divisional application Serial No. 399,585, ~iled March 26, 198~.
Turning now briefly to a discussion o~ 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 mab/,~
~731~
the clutch housing 131 and within the reservoir 241, and the fact that the same lubricating fluid may be utilized to urge the crusher se-tting indicator rod 281 upward, have already been discussed. Nevertheless, it is believed appropriate at thi.s po.i.nt 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 reamins inactive but, rather, -that the overall lubrication system, some portions oE which are not il lus tra ted, i s a ~ ons tantly i rcu: atln-l sys tem .
.~
~, - 2~ -mab/
' ~4'731~
:
As a starting point, it may be noted $hat 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 ~nd the radially inner portion of the eccentric 91. The lubricating fluid is further conducted along the path indica~ed at.l27 and coats the bearing surface between the support cone bearing 129 and the support cone bearing seat 125.
1~ 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 41f the lower portion.of the bevel gear drive assembly 73 and the upper portion.of the shat 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 fil-tration 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 c.irculating supply of clean lubricating flui~.
It will be understood that the foregoing description of the preferred e~bodiment of the present invention is for purposes of illustration only and that ~he various structural and operational featwres as herein disclosed.are susceptible to a number of modif ications and changes none of whi~h.entail any departure from the spirit and SCOp2 of the present invention as defined in the hereto appended claims~
~ - 29 -pc/,~
Claims (7)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A crusher setting indicator for a cone crusher, which crusher includes a moveable mantle and a stationary concave, comprising:
a rod, supported by said crusher, arranged for linear movement, the position of said rod along said line of linear movement being directly related to the position of said mantle along said line; 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.
a rod, supported by said crusher, arranged for linear movement, the position of said rod along said line of linear movement being directly related to the position of said mantle along said line; 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 crusher includes a cone support bearing seat arranged for movement along said line and one end of said rod is in abutting relationship with said seat.
3. A crusher setting indicator according to claim 2 further comprising biasing means coupled to said rod for biasing said rod into said abutting rela-tionship with said seat.
4. A crusher setting indicator according to claim 3 wherein said biasing means comprises a piston ring.
5. A crusher setting indicator according to claim 1 wherein said crusher includes a center hub having an axially extending path formed therein, said rod being positioned within said path.
6. A crusher setting indicator according to claim 5 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.
7. 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 gear bearing a plurality of teeth, said gear teeth and rod teeth being positioned for engage-ment with one another.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000399584A CA1147318A (en) | 1979-09-17 | 1982-03-26 | Fabricated cone crusher |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000335731A CA1137451A (en) | 1979-09-17 | 1979-09-17 | Fabricated cone crusher |
| CA000399584A CA1147318A (en) | 1979-09-17 | 1982-03-26 | Fabricated cone crusher |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1147318A true CA1147318A (en) | 1983-05-31 |
Family
ID=25668962
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000399584A Expired CA1147318A (en) | 1979-09-17 | 1982-03-26 | Fabricated cone crusher |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1147318A (en) |
-
1982
- 1982-03-26 CA CA000399584A patent/CA1147318A/en not_active Expired
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