CA1137451A - Fabricated cone crusher - Google Patents

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 moveable mantle and the stationary concave of the crusher includes a rod supported by the crusher, the rod abutting the cone support bearing seat of the crusher, the position of which seat is directly related to the position of the mantle. A pinion gear is coupled to the rod and the orientation of the gear is used to provide an indication of the distance between the mantle and concave.
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 and from the entire disclosure.

Description

B1~CXGROU~D O~ T~E INVI~NTION

This invention relates to cone crushers and more particularly to such crushers ~ich have fabricated upper and lower main frames.
In addition, this inventio~ relates to such cone crushers which include anti-spin mechanism5 and crusher setting indicatorsO
Cone crusners, which are deviczs well known in the art, are aevices which are adapt2d to receive large ~ieces of hard materia~ _ such as, ror exam~le, large chunks of rock and to reduce them to a large numb-r of smaller pieces which are of a generally uniform size. The crushers which are presently widely used in the concrete and aggregate indust~y have numerous characteristics which maXe them less than ideal For ex~mple, such crushers must have extra-ordinarily strong main framss due to the fact that they are subject to extreme mechanical stresses. For this reason, among others, such crushers have generally been provided wi~h cast frames. Al-though such cast frames have generally proved to be of sufficient strength, the cost Oc their manufacture is quite high and they are therefore, from an economic point of view, less than completely satisfactory. In an effort to overcome this negative aspec~ it has been proposed to abricate the lower portion of the main frame of such a crusher from pre-formed components rather than to cast it and to thereby obtain substantial savings. An example of such a cone crusher which includes a fabricated lower main frame portion is provided in U.S. Patent No. 3,150,839. It is noted, however, that even this patent teaches a crusher main frame structure which includes cast me~bers, in particular, this patent teaches a structure utilizing a cast ce~ter hub. The industry, recognizing the advantages of fabricated main frames for crushers has attem~ted .
,, ' ' ' ' '~
.

.. . .. .... . ...

to ?rovide main frame structures which are completely fabricated, that is, contain only plate and forged members and contain no cas. membars An example of a crusher frame ~hich is construe.ea ~rom only rabricated memb~rs is provided by U.S. Patent No. 3,843, 006 ;hic;~ is fabricated solely from pre-'ormed components which are wel~~d tog-.her. Such structures, although p~oviding definite advan.ages over ths earlier cast structures are nevertheless not com?le,ely sa.isfactory in tha. they frequently require great n~bers of components to fullfill their function~ For example, .he last noted paten. includes an adapter plate for permitting the mating o~ the center hub with the countershaft which houses the required motor drive shaft. Clearly, this results in less than a completely satisfactory solution to the problem beeause h greater nlmber o} prefabricaied sec-tions requires a greater numb~r l; of ~elds. ~nis, in turn, provides the opportunity for unsatisfaet-ory welds and results in increased expense in that each o~ the welds must be (or should be) inspected either by X-ray or ultra-sonic tecl~niques or bothO
~ As indieated above, the function o~ 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 erusher, the magnitude of the crushed material which will be provided by the erusher unit, that is, the erusher -set.ing. Presently Xnown crusher setting indieators are not,

2~ however, completely satisfactory in that they are either mechan-ically complex and expensive or they do not provide inormation regarding the size of the material to be provided by the erusher witn a desired degree of accuracy. It is, of course, possible ~o accurately and inexpensively determine the erusher setting by .

. ~ .

.. .... . .. ... . ., .. ., , , , _ _ _ _ _ measuring the si~e of the material after it passes through the crushing ch~ber and is emitted from the crusher but such informa-tion is obviously of less utility than is ~nowledge of the crusher setting prior .o oparation of the crusher.
Cone crushers of the typ~ here under discussion include a gyratory memb-r generally referred to in the art as a mantle. ~ue .o the construc~ion of the crusher, the gyrating mantle has a ten-dency ~o ro,a~e ln a first direction when the crusher is not under load, that is when the crusher is not in the process of crushing material. Further, the mantle tends to rotate in a second direction, opposite to the first direction, when the crusher is under load.
As is well known in the art, rotation of the mantle in the first (no load) direction is to be avoided because such rotation can cause addi~ional 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 kno~n frequently are in the form of devices which absolut-ely bar the rotation of the mantle in the first direction while permitting the mantle to freely rotate in the second direction. Tke utility of such mechanisms has proved to be less than co~pletely satisfactory because absolutely barring the rotation of the mantle in the first direction, may, under conditions where the mantle is being urged in the first direction with sufficient force, resul~
in the destruction of components of the crusher~
SU~ RY OF THE INVENTION
It is therefore an important object of the present invention to provide an improved cone crusher structure by means of which the aforesaid drawbacks and disadvantages may be most efficacious-ly avoided.

_, . . . . . .. ... .... _ .. . .

. .

It is a further object of the instant invention to provide a cone crusher in which the upper main frame portion is constructed only from prefabricated components.
It is yet another object oE the instant invention to provide a fabricated frame for a cone crusher which is equally as strong as a cast frame.
It is still another object of the instant invention to provide a fabricated frame for a cone crusher which includes a minimum number of components.
! 10 It is yet a further object of this invention to provide a fabricated frame for a cone crusher which can be manufactured at a minimum cost.
Generally speaking, the objects of the instant inven-tion are attained by the provision of a fabricated upper frame for a cone crusher comprising a first annular member, a first tubular member extending orthogonally relative to the first annu-~ lar member, the tubular member having first and second ends and ; being fixedly connected, at the first end thereof, to the first annular member, a second annular member being oriented so as to be generally parallel to, and spaced from, the first annularmember, the first tubular member being fixedly connected, at the second end thereof, to the second annular member, a third annu-lar member being oriented to be generally parallel to, and spaced from, the second annular member, and a first plurality of cir-cumferentially spaced ribs fixedly connected between the second and third annular members.

Pg/~ - 4 -113~4S~

In a specific embodiment of the instant invention there is provided a fabricated frame for a cone crusher comprising a first annular member formed with a plurality of circumferentially spaced axially oriented holes extending therethrough, a first tubular member extending orthogonally relative to the first annular member, the tubular member having first and second ends and being fixedly connected, at the first end thereof, to the first annular member, a second annular member being oriented so as to be generally parallel to, and spaced from, the first annular member, the first tubular member, being fixedly connected,.
at the second end thereof, to the second annular member, a third annular member being oriented to be generally parallel to, and spaced from, the second annular member, a first plurality of circumferentially spaced ribs fixedly connected between the second and third annular members, a tubular center hub, a fourth annular member, having a slot formed therein, oriented ortho-gonally relative to the longitudinal axis of the hub, the inner periphery of the fourth annular member being fixedly connected to the hub, a second tubular member, having a slot formed there-in, extending orthogonally relative to the fourth annular mem-ber, the second tubular member being fixedly connected, at one end thereof, to the fourth annular member, a fifth annular mem-ber, formed with a plurality of circumferentially spaced axially oriented holes extending therethrough, oriented ~enerally parallel to the fourth annular member, the fifth annular member being fixedly connected, at the inner periphery thereof, to the second tubular member, a third tubular member, having an aperture form-ed therein, oriented to extend orthogonally relative to the fifth Pg/) ~ - 5 -11374Sl annular member, the third tubular member being fixedly connected, at one end thereof, to the fifth annular member, and a fourth tubular member oriented so that its longitudinal axis extends generally orthogonally relative to the longi-tudinal axis of the third tubular member, the fourth tubu-lar member adapted to extend through the aperture formed in the third tubular member and the slots formed in the fourth annular member and the second tubular member, the outer peri-phery of the fourth tubular member being fixedly connected to the walls of the apertures and the slots, the plurality of holes formed in the first annular member being arranged for alignment with the plurality of holes formed in the fifth annular member, whereby the first and fifth annular members are adapted to be removably connected to one another.
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 con-junction with the accompanying drawihgs, in which:
BRIEF DESCRIPTION OF THE_DRAWINGS
Fig. 1 is a cross-sectional plan view of the cone crusher of the instant invention;
Fig. 2 is a detailed cross-sectional plan view of the anti-spin mechanism of the instant invention;
Fig. 2A is a schematic representation of the anti-spin mechanism shown in Fig. l;

pg/l,~ - 6 -11374C~

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 invention;
Fig. 6 is a detai]ed cross-sectional plan view of the sealing arrangement of the instant cone crusher; and Fig. 7 is a cross-sectional plan view taken along lines 7-7 of Fig. l;
DESCRIPTION OF THE PREFERRED EMsODIMENT
Referring now to Fig. 1 there is illustrated the cone crusher of the instant invention. The crusher includes a frame which is in two portions, that is, upper and lower main frame portions, these portions being bolted together to form the crusher main frame. Turning first to the upper main frame portion, there ;s illustrated Pg/,~ - 7 -:
- ' ~ - :
- ' 1~374Sl a feed hopp2r (although feed hoppers are g2nerally considered by tha art to be sep~rate from, and not ~orm part of, a crusher frame, the fe-d hopper herein will be described as if it formed part of the upper main frame portion) generally indicated at 1 which includes a ~abricated tu'~ul2r me~ber 3, which member may be fabricated from b-nd rolled steel pla~e. A fabricated member 5, which has the g-neral cross-sectional configuration of a truncated cone and a lab-icated me~ber 7 which also has the genaral cross-sectional con-fi~ralion of a truncated cone are both welded, at iheir upper per-iphe-ies, to the me~ber 3 The members 5 and 7 are also welded .o one another along their contiguous leng~hs, it being noted that '.he member 5 is longer than the member 7O A fabricated tubular member 9 is w21ded at its u~per periphery to the lower periphery of the tr~ncated member 5 and to the side of the member 7 The tubular membar 9 is further welded, at its lower periphery, to an annulus 11, the combination of the tubular member 9 and annulus 11 having an L-shaped cross-sectional configuration. The annulus 11 is formed with a plurality of holes therein and it is thereby adapted to be firmly affixed to an annulus 13, which is formed with a plurality Oc countersunX 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 conLiguration of a truncated cone is cast from an extremely hard and long wearing material such as, for example, manganese ste~l, and it is formed with a plurality of gripping or hooX members, one of which is indi_ated at 19. The concave 17 is main~ained in position by a plurality of gripping members 21 which pass through apertures 20 formed in the annulus 13, which gripping members 21 may have any desired configuration. In the embodiment ., ~ .
_ ~ _ ', ' '.

.. _ .,~ . , . . .. . .. . . ....... _ _ _ . .. .. _ _ ...... _ . .. - . _ .

illustrated in Fig~ 1, the gripping members 21 each have a "T"
shaped cross-section although a mQmber having a "J" shaped cross-sectioa could also be utilized Conventional tightening nuts, such as those indicated at 22 serve to dra-~ the gripping members 21 up~a-;dly, thoreby dra~ing the concave 1~ upl~ardly to its desired position An annulus 2~, oriented so as to b~ parallel to both the annuli 11 and 13 is positioned in the vicinity oE the lower end of the concave 17.
A plurality of gussets or ribs 25 which are oriented orthogon-0 211y ~ith respect to th~ annuli 13 and 23 are weldod to the annuli 13 and 23 so as to form a rigia support therebetween. The ribs 25 are equally spaced circumferentially and there may be, for example, 16 such ribs spaced 22.5 apart, as clearly seen in Fig. 4; A
plurality of the ribs 25 are formed with apertures 27 therethrough 1~ so as to facilitate the lifting of the upper portion of the fab-ricated main frame of the crusher when separation of the upp-r 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 ~ith apertures such as the one indicated at 27.
A fabricated tubular member 29, which may be formed of bend rolled sheet steel, i9 welded at its upper periphery to the annulus 23. Apertures such as the one indicated at 33 are forme~
at various locations about ths periphery of the tubular member 29 which apertures may be blocked by, for example, hinged doors such as the one indicated at 35 so that access may be had to the inter-ior of the crusher ~hen 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 circumfsrence C~.

... ..... .. ... . , ., .. ~ ., .. ~

' ' ' .

1137~5~ .

of the upper main frame portion of the crusher. The ribs 30, which have "U" shaped cross-sectional conEigurations (the open ends of the "U"
abutting the tubular member 29 and the closed end of the "U" extending in a radially outward direc-tion) 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 ~ade of a long wearing material such as low carbon steel and which may be formed by rolling, is tac~ welded at a number of points to the radially inward surface of the tubular member 29. The wear liner 31 serves to reduce the wear of the tubular member 29 which would be caused by the action of the crused material being processed by the crusher unit and~ of course, the liner may be removed and replaced when necessary. A number of ribs or gussets 32, for example, eight such gussets, are welded to the annulus 23, the tubular member 29, and the wear liner 31 so as to combine the annulus 23, the member 29 and the liner 31 into a rigid structure. A horizontal annulus 37 is welded to the lower peripheries of the tubular memker 29 and the "U" shaped rib 30. The annulus 37 is formed with a plurality of apertures 38 formed therein through which bolts may be passed for attaching the just described upper main frame portion to the lower main frame portion of the cone crusher, which lower portion will be described in detail below.
Turning now to a description of the lcwer main frame portion and referring to Fig. 1, it is seen that the lower main frame portion includes a forged steel center hub 41 which has an annular shoulder 43 formed at the upper end thereof. An annuIus 45 (which is illustrated in Fig. 7 and which will be described in greater detail below) is welded to the hub 41 at the shoulder 43 and a fabricated tubular member 47, which may be, for example, of bend cg/~J

~137D,S~

rollcd steel plate, is ~elded to the annulus 45 at the outer per-iphery thereof. Pn a~nulus 49, oriented to e~tend orthogonally relati-~e to the member 47 i9 t~elded thercto interjacent the ends thereoL. The annulus 49 is formed ~ith a plurality o~ apertures 51 being so located as to be in alignment ~ith the apertures 38 ~hich e~tend throusn the annulus 37. It may thereCore be seen that the annuli 37 and 49 may be rigidly aLtached to one anothsr by, for e~ample, a bolt and nut combination such as indicated at 53 thereby accomplishing the connection of the upper and lower main Crame porLions~
A plurality of ribs or gussets 61, for example, three (most clearly seen in Fig. 3), are welded to the forged center hub 41 and to a fabricated tubular member 63 which may be formed oE bend rolled sheet steel. The tubular membsr 63 extends orthogonally relative to the annulus 49 and the member 63 is welded, at its upper periphery, to the annulus 49. In addition, the ribs 61 are welded to the annulus 45, to the tubular member ~7 and to the annulus 49, thereby imparting substantial strength and rigidity to the fabricated lower main frame portion.
A driving mechanism is, as is conventional, provided for the crusher of the instant invention in a manner which will be explain ed 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 circulæ
aperture in t`ne tubular member 63, the aperture formed extending- -through the tubular member 47 and the annulus 45. It will be understood of course that the annulus 45 may either be provided as a complete annulus, a portion subsequently being removed therefrom, or, alternatively, the annulus 45 may originally be formed as a j1 ' _ ~ _ .

'' 11374Sl 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 indicat~d generally at 71, is of any conventional form and may be used to drive the inventive crusher in any conventional manner For example, the embodiment of the invention illustrated in Fig. 1 shows the drive shaft 71 driving the cone crusher by means of a conventional bevel gear which is indicated ~enerally at 73.
As was noted a~ove with respect to the ribs 61~ a num~er of ribs 67, in this embodiment, two (most clearly seen in Fig. 3), are welded to the center hub 41, the tubular member 63 and to the tubular member 69. m e ribs 67, therefore, also impart substantial strength and rigidity to the fabricated lower main frameportion and diffeP frcm the ribs 61 only in that the ribs 67 do not extend upwardly to the annulus 49 as do the ribs 61, the ribs 67 terminating at the drive shaft housing member 69.
Thrning now to a description of the internal structure of the cone crusher, it is seen that the cr~sher includes a forged shaft 81 having at least two lubrication paths 83 formed therein~ Additional lubricational paths, such as those indicated at 85 are also formed in the shaft 81. It is also appropriate to note at this point that the tubul æ
hub 41 is formed with a stepped bore indicated at 82. 'rhe stepped bore 82 is formed with an internal dia~eter 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 o~eration of the crusher, is an eccentric sleeve 91. m e eccentric sleeve 91~ which is driven by cg/~

11374LS~

the drive shaft 71 -throu~h the mechanism of the bevel gear 73, extends up~ardly to a point beyond the uppermost portion of the shaft ~1 ~nd do-~n~ardly to a bearing 93 ~hich is in turn supported by tho hub al, the bearing 93 facilitating the rotation of the eccent~ic sleeve about the shaft 81. To reduce the wear of both the shaft 81 and tha eccentric 91, a bearing of relatively soft alloy metal may be ~osi-cioned bet~een the adjacent bearing surfaces of the shaft 81 and the eccentric 91, Alternatively, a layer of relatively soft alloy metal, such as, for example, an alloy includ-0 ing lead, tin and an.imony may be coated onto one or bo~h of the bearing surfaces as is the case in the embodiment illustrated.
T'ne interior of the tubular shaft 81 serves as a piston chamber, indicated at 95, and a piston 97 is positioned therein The piston 97 is actuated by hydraulic fluid which is provided by a ~5 mechanism, not sho~, through a conventional tubing and coupling combination, generally indicated at 99, to a section of convention-al tubing indicated at 101. The tubing 101, together with a con-ventional hydraulic coupling, extends through a passage, indicatea at 103, formed in the hub ~1 and the shaft 81. The tubing 101 extends at its other end to a coupling 105 by means of which it is connected to an accumulator 107. The accumulator 107 is supported by a frame, indicated generally at 108, The frame 108 is attached to the lower portion of the main frame by any conventional means such as, for example, a clamp indicated at 110. It is here appropri ate to note that, for reasons which will be discussed below, a gas containing bag 111 is positioned within the hydraulic fluid accumul-ator 107. As previously noted, the interior of the shaft 81 serves as the piston chamber 95, and as illustrated, ~he chamber extends through the bottom of the shaft 81. To prevent the hydraulic fluia within the chamber 95 from exiting through the bottom of the shaft '. 1~ . ' , .
.

' ..: ~.,.., .. ,, '',.

113745~
81 a oonventional plug or bleeder flange 113 is insertecl 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. ~n air tube 115, supported at its lc~er end by the plug 113, extends into the piston chamber 95 and up to the bottom of the piston 97. The tube 115 terminates, at its lc~er end, in a valve 117 positioned, for protection, in a groove in the plug 113. In tnis manner air trapped below the piston 97 may be released into the atmosphere throuqh the valve 117.
Supported by the piston 97 is a support cone bearing seat 125 which may be affixed to the piston 97 by any conventional means such as a plurality of screws, one of which is illustrated. ~ormed in the support cone bearing seat 125 is a lubrication passage 127 which is aligned with the lubrication passage 83 formed in the shaft 81. Supported by the support cone bearing seat 125 is the support cone bearing 129 and supported by the support cone bearing 129 is a clutch housing 131.
Supported by and attached to the clutch housing 131 is a support cone 141 which support cone is supported by a circular shoulder 142 formed at the lower end of the clutch housing 131. m e support oone 141 is in annular abutting relationship with the eccentric sleeve 91 and the support cone 141 extends dc~nwardly for almost the entire len~th of the sleeve 91.
ID reduce the wear of both the sleeve 91 and the support ccne 141 a layer of relatively soft alloy metal is coated onto one or both of the bearing surfaoes of the oone 141 and the sleeve 91.
A steel flywheel 148 is connected to the eccentric 91 by~
for exampler a bolt such as the one indicated at 152 and the flywheel 148 is arranged to rotate with the eccentric 91. Connected between the support cone 141 and the flywheel 148 is a grease filled lab~rinth seal indicated generally at 161, the pu~pose of cg/ ~
i whicll is to prevent grit such as particles of rock, rock dust, ~tc.
from entering the internal structure of the cone crusher where s~ch particles ~:ould cause excessive wear~ The labyrinth seal includ~s a pluralit~- of .ubular sealing rings 163. In the er~odi-men' here illustr~'ed, there are four such rings 163, two of which are upper sealin~ rings, e~tending do~n~ardly from the support cone lal and t~;o of ~hlich are lo~er sealing rings, each of w`nich extends upward'y from t~e fl~heel 148~ It ~ill be noted thai the sealing rings 163 are arranged in an interlacing relationship so tha, greas- inject~d in.o .he voids betwean the rings 163 will e~~ective-ly prevent grit from entering the internal structure of the crusher.
As most clearly illustrated in Fig~ 6, one or more grease fittings, indica.ed at 165, are provided about the periphery of the labyrinth seal 161 and these fittings 165 are connected, by means of tubing 1~ 167, to a port 169 formed in the radially outwardmost one of the sealing rings 163. A wear collar 181, uhich collar may be mada of low carbon steel, is welded to the support cone 141, the collar 181 extending generally in the area of the upper hal~ of the seal 161. The wear collar 181 thus prevents damage to the labyrinth seal structure 161 which n~ight be caused by crushed material, ~7hich has passed through the crushing chamber, striking the sealing rings 163.
Supported by the support cone 1~1 is a mantle 191 which has the cross-sectional configuration of a truncated cone. Supported by the uppermost portion of the mantle 191 is a collar 193 which-has a generally flared tubular or bell-li~e 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 hydraullc nut assembly 113745~

195 is a feed plate 197 which may be made of low carbon steel. The plate 197 serves to distribute the material provided to the crusher evenly about the crushing c~amber 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 ont the externally-threaded clutch housing 131 forcing the collar 193 down~7ardly and thereby urgingthe mantle 191 into snug engagement with the support cone 141. Ib increase the downward force applied by the collar 193 to the mantle 191, a hydraulic pump, not shown, applies, Via tubing 203, hydraulic fluid under pressure to a chamber bounded by the lcwer 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 downw ædly.
The nut 201 cannot, however, move upw ædly because it is threaded onto the clutch housing 131. The pressure of the hydraulic fluid thus forces the collar 193 downwardly. When the syst~m has been pressurized to a desired degree (the collar urged downward with a predetermined force)~ a lock nut 205 is threaded onto the outer periphery of the nut 203 (which nut 203 is threaded externally as well as internallyl ! until the nut 205 is snug against the collar 193. At this time the hydraulic pressure may be released and the nut 2Q5, the nut 201 and the coll æ 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. m e 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-surf~ace of the feed plate 197, thereby permitting screws, such as the one indicated at 209, to hold the feed plate in position.

cg/ ~

~137~51 SuFported by the support cone bearing seat 125 and connected thereto by a oonven-tional universal joint 219 such as, for example, a Hooke's joint, is a shaft 221. The shaft 221 is connected, by means of a conventional universal joint 223 to an anti-spin mechanism, indicated generally at 225. The anti-spin mechanism 225, which is most clearly show.n in Fig. 2, includes a hydraulic motor or pump 231. The drive shaft of the motor is connected, by means of the oollar 233, to the universal joint 223. Fixedly p~sitioned 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 the lubricating oil filled reservoir 241 .
are a manifold 243, a check valve 245, and.a relief valve 247, each of which is conventional and which may be hydraulically coupled in any conventional manner. For reasons which will be discussed below a length of tubing 249 extends frcm the manifold to the lower portion of the reserv~ir 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. 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 cg/~/

~37451 obviously be utilized. For example, an arrangement wherein the relief valve, the check valve and the manifold are vertically arranged at one side of the reservoir 241, with the relief valve being positioned uppermost and the manifold being positioned at the bottom of the reservoir chamber, would clearly provide an equivalent structure. The shaft of the motor 231 which is, as previously noted, coupled to the shaft 221 by means of the universal joint 223 does not rotate. Rather!
the motor 231 is arranged for rotation. The motor, by means of the motor housing fixedly connected thereto, is connected directly to the clutch housing 131 and it will therefore be obvious that the rotation of the clutch housing, the support oone 141 and the mantle 191 will be directly related to the rotation of the motor 231. Alternatively, however, it may be desired to attach the motor housing to a conventional base plate which could, for example, take the form illustrated in Fig. 2 at 261 and to attach the base plate 261 to the clutch housing 131, thereby accomplishing the same end.
Turning now to Fig. 5, there is illustrated, in detail, the crusher setting indicator of the instant invention. The crusher setting indicator includes a tubular rod 281 which is located within the lubrication path 83 formed in the shaft 81 and the rod may be made of any suitable material, for example, steel. me uppermost portion of the rod 281 is in oontact with the support cone bearing seat 125 and its lowe~most portion, indicated at 285, extends into a lubrication fitting 283 located just below the lowermost portion of the lubrication path 83. It is appropriate to note at this point that the rod 281, which is located within the lubrication path 83, is tubular so that the rod itself may serve as a portion of the path for the lubricating medium. me 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

~ - 18 -cg/ ~

~13745~

pinion gear 291 is mounted on any convenient support, for example, on a plate extendiny from the bleeder flange 113. The pinion gear 291 is arranged for rotation about a shaft 293 which shaft is in turn supported by the plate 289 and the pinion gear is positioned so that the teeth thereof engage the teeth 287 of the rod 281.
As previously noted, and as seen in Fig. 1, the support cone bearing seat 125 is in direct contact with, and is vertically supported by, the support cone bearing 129. Further, the bearing 129 ~ -is coupled, with respect to vertical movement, to the mantle 191, through the clutch housing 131 and the support cone 141. It will therefore be understood that the vertical location of the rod 281, which is arranaed for linear vertical movement corresponds directly to the vertical position of the mantle 191. The vertical position of the rod 281 may therefore be used to indicate the crusher setting, that is, the size to which the cone crusher will reduce material provided thereto. For the purpose of providing a direct calibrated crusher setting reading the pinion gear 291 may be o~upled in any conventional manner desired to any conventional reading apparatus. Thus, for example, the pinion gear 291 might be used to directly drive a needle type indicator which is calibrated relative to the diameter of the material processed by the crusher. Alternatively, the rotation of the pinion gear 291 might be used to drive an intermediate transducer of any suitable type which would, in turn, provide an indication of the size of the material discharged by the crusher.
At this time it is appropriate to note that for the rod 281 to provide correct crusher setting readings it is necessary that the rod 281 be maintained in an abutting relationship with the bearing seat 125. It will therefore be understood that it is ne oe ssary to provide a mechanism w~ich will bias or urge the rod 281 upwardly so that it is maintained in direct contact with the undersurface of the bearinq cg/ ~

.
;

11374S~ .
seat 125. In the embodiment illustrated the biasing mechanism includes a pair of sealing rings (acting as piston rinqs) 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 convent-ional manner. One or more ports 305 are formed in the wall of the rod 81 thereby permitting a portion of the lubricating oil flowing through the rod to pass into the (piston) chamber formed between the rings 301 and 303. The lubricating oil, which is always flowing into the lubrication path 83 (the rod 281) under pressure, thus provides an upward force which acts upon the ring 303 urging it upwardly, thereby urging the rod 281 upwardly and maintaining the uppermost end of the rod in abutting contact with the undersurface of the bearing seat 125. To accomodate the rings 301 and 303 and to provide r space for the vertical movement of the ring 303, a stepped bore, indicated at 307, is provided in the shaft 81. The stepped bore, which has a diameter greater than the diameter of the remainder of the bore (the lubrication path 83) of the shaft 81, extends, it will be noted, only a distance sufficient to accomodate the excursions of the rod 28i. Upward movement of the ring 303 within the stepped bore will, of course compress any ambient air trapped between the uppermost portion of the stepped bore and the ring 303. Inasmuch as such compression of ambient air would cause undesired resistance to the upward movement of the cg/ f~

11374S~

rod 281, ~ ven~ing port, indicated at 30~, is prov~ded in the shaft Bl. The p~rt 309, i~hich extends into the stepped bore 307, permits air which wOuld other~ise b~ trapp2d to escap2, thereby permitting ~he rod 231 to mo~e up~ard more -asily.
of colrse, the ;-od 281 rnay b~ maintained in abutting relation-sh~p with the b2aring seat 125 by othe~, e~uivalent arrangem2a~s, not sh~wn. For example, the upper por~ion of the bore of the shaft 81 could be enlarged and the bot-tom o' a spring could be fixedly positioned a~ the lower terminus of the enlarged bore. In this arrangemen~ a collar coula be îixedly connec~ed 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 compre~-sing the spring between the lower terminus of the enlarged bore and the collar attached to the rod 281. Tha 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 under3to3d that such para-meters would, in part, be dependent upon the weight of the rod and the dlstance between the coIlar and the lower terminus of the en-larged bore. It is ihus seen that an arrangement utilizing a spring to maintain the uppermost portion of the rod 281 in contact with the underside of the support cone bearing seat 125, which spring arrangement is a viable alternative for the piston arrange-V
ment illustrated, has been described.
2; Turning now to Figv 6, the flywheel 148, the uppermost part of the tubular member ~7, a labyrinth seal 150 and the telescoping labyrinth seal 161 are shown in greater detail The flywheel 148, w'nich ma-~ be made of steeI, i9 bolted (as indicated at 152 in Figv 1) to the lo-~er portion of the eccentric sleeve 91 and rotates 33 therewith. To prevent grit, for example, rocX dust, from entering ',~

...... . ....... ._ ..... _ .__.. ___~__ = _ . .

1137~S~

into thc interior of the crusher through the space be~ween the ro-tating flywheel 1~8 and the stationary member 47, the ~rease filled labyrinth seal, indicated at 150, is prov;ded. A grease path 321, which is connected to a standard grease fitting 323, is formed ~ hin the memb2r ~7, thus providing a path throug'n ~hich srease m2y be inje_te!l inlo the voids of the seal. It is appropri-ate .o note at this p~int, because it is most clearly sho~n in Fig. 6, that tih2 lower sealing rings 163 are connected by, for example, screws such as the one indicated at 331, to the flywheel 1a8~ Tn this m~nne- the recuired support for the lower sealing rings 163 of the labyrinth seal 161 may be provided.
Turning now briefly to Fig. 7, the slotted annulus 45 is illustrated in detail. In particular, it will be noted that the tubular me~bar 69, tYhich forms t'ne housing for the driva shaft 71, is welded to the walls of the slot, which slot is indicated at 341. In addition, Fig. 7 clearly illustrates the annular nature of, and the concentric relationship bet~een, the sha t 81, the hub 41, the hub shoulder 43 and the annulus 45.
OPERATIO~ OF THE CRUSHER
As previously indicated, the function of the crusher is to receive large pieces of hard material and to reduce ~he large pieces to a number of smaller pieces of relatively uniform size.
In operation, chunks of a material such as rock are fea into the feed hopper 1. The pieces of rock drop into the crushing chamber, 2~ t~hich is defined by the area bounded by the concave 17 and the mantle 191, ~here they are then crushed, or com~ressed, or fractur-' ed by striking one another, resulting in their brea'~age into small-er pieces. 'The size of thè pieces passing through the crushing chamber and out of the crusher unit is determined by the space between the mantle 191 and the concave 17. This space or distance a~ . . .
:
, is in turn controlled, as previously indicated, by the piston 97. As is d ear fram Fig. 1, linearly upward movement of the piston 97 eauses the mantle 191 to move upward, that is, closer to the concave 17, whereas lowering the pistan 97 eauses the mantle 191 to move dc~nward, further frc~n the stationary concave 17. Tb effect the vertical movement of the mantle 191, hydraulic fluid is pumped into, or withdrawn, throucih the tubing and coupling ccmbination 99. After the mantle 191 has been positioned at the vertical level desired, the oambination 99 is effeetively removed frem the system by, for example, closing a valve (not shown) and the vertical position of the mantle 191 is thus set.
As is well known in the art, hc~wever, large pieces of material whieh are too hard to be crushed treduced in size) by the action of the rnantle and eoncave oeeasionally enter the unit. It is because of this faet that the aeeumulator 107 and the gas filled kag 111 are prc)vided. In the event that a large piece of excessively hard material (frequently referred to in the art as "tramp metal") is prc~vided to the erusher, the mantle 191 will obviously ke forced dc~nwardly. The dc~nward movement of the mantle will, in turn, eause the piston 97 to move dc~nwardly, thereby foreing same of the hydraulie fluid in the piston ehamber 95 and/or the tubing 101 into the aeeumulator 1070 (it having been noted above that the combination 99 has been effeetively removed from the system). Because hydraulie fluid is not eompressible, while gas is, the inereased pressure on the gas in the bag 111, eaused by the inereased quantity of hydraulie fluid in the aecumulator 107! will eause the ecmpression of both the gas bag 111 and the gas therein.
After the mantle 191 has been foreed downw æ d by the tramp metal a distanee suffieient to permit the tramp metal to pass between the mantle 191 and the ooneave 17 (and the metal is passed by the erusherl, the ecmpressed gas in the gas eg/ ~

~137451 bag 111 ex~ands, 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 cha~ber.
As just noted, the size of the material passed by the cone crusher is dependent upon the spacing between the mantle 191 and the concave 17. Clearly, it is desirable to be able to determine, prior to the operation of the crusher, the size of the pieces which the crusher will provide. Although the structure of the crusher setting indicator has already been discussed in detail with regard to Fig. 5, it is believed appropriate at this time to briefly explain the procedure involved in calibrating, or "zeroing", the crusher setting indicator.
As is well known in the art, it is relatively easy to determine the vertical position or height to which the piston 97 has raised the support cone bearing seat 125. m e mantle 191 undergoes continuous wear, however and thus merely knowing the height to which the seat 125 has been raised is insufficient to permit an operator to accurately determine the distan oe 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 maxlmum height which is, of course, the height at which the mantle 191 contacts the conca~e 17. Under such conditions it is a simple matter for the operator to "zero" a gauge or other indicator controlled by the pinion gear 291 so as to indicate "zero", that is, the absence of space between the concave and mantle. m e op~rator may then lower the piston 97 and the indicator controlled by the pinion gear will accurately reflect the true vertical distance between the concave and mantle. In this manner the described crusher setting indicator compensates for mantle and concave wear and accurately reflects the true spacing therebetween.

3~

cg/~"

1137~5~

As previously noted, the size of the material provided by the crusher is determined by the distance between the mantle 191 and the concave 17. The reducing action of the crusher is, however, as is well known in the art, provided by the gyration of the mantle relative to the concave, the gyration of the mantle having the effect of constantly increasing and decreasing the space between the mantle and the concave.
Ihe desired gyratory motion of the mantle is here provided for by the rotation of the drive shaft 71 which causes the eccentric sleeve 91 to rotate about the stationary shaft 81. Because the sleeve 91 has an eccentric configuration, as illustrated and is conventionally known in the art, the support cone 141 and the mantle 191 firmly affixed to the cone 41 will gyrate.
At this point it is appropriate to discuss the operation of the anti-spin mechanism 225 and it is noted that the structure and operation of the mechanism is most clearly shown in Figs. 2 and 2A.
As previously indicated, the mantle 191 gyrates due to the rotation of the eccentric 91. It is well known in the art, ho~ever, that the mantle 191 also rotates as the eccentric 91 rotates notwithstanding the fact that the beæing 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 p æticular, it is well known that when the crusher is operating in a "no-load" condition, that is, the eccentric 91 is driven and no material is being fed to the crusher unit, the mantle 191 tends to rotate in the same directien as the eccentric 191. It is further known in the art that ~hen 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 CC~/ ru ~

S~

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. Ib prevent mantle rotation in the no-load direc-tion the anti-spin mechanism 225 is utilized. In particular, the anti-spin mechanism is arranged so that the mantle 191 may rotate in the load direc-tion but will be prevented (within limits which are more fully discussed below) from rotating in the no-load direction.
Referring now to Figures 2 and 2A, it will be understood that when the crusher is under load the motor 231 is caused to rotate in the "load" direction by the rotation of the clutch housing 131 which is fixedly connected to the support cone 141. The rotation of the motor 231 in the load direction causes the lubricating fluid within the reservoir 241 to be drawn upwardly through the check valve 225 and the fluid is returned to the reservoir throu~h the manifold 243 and the tubing 249.
However, when the motor 231 is caused to rotate in the no-load direction the lubricating fluid is drawn into the manifold 243 through the tubing 249. The fluid cannot, however, be returned to the reservoir chamber through the check valve 245 because it is a unidirectional valve.
Furthermore, the fluid cannot be returned to the reservoir chamber through the ball-type relief valve 247 because the valve 247 is biased closed by the action of a conventional spring loaded mechanism, not shcwn.
In this manner the motor 231 is prevented from rotating in the no-load direction and the mantle 191 is therefore also barred from rotating in the no-load direction. In the event, however, that the mantle 191 is urged to rotate in the no-load direction with sufficient force (urging the motor housing 231 to rotate in such direction as well) then, rather than risk the possible cg/
~ .

:

11~7~S~ .

breakage of components of the crusher, the motor 231 is permitted to rotate in the no-load direction, thereby permitting the mantle 191 to also rotate in the otherwise undesired direction. Tb accomplish this end the spring maintaining the relief valve 247 in a closed condition is so selected as to permit the lubricating f~uid to open the yalve 247 when the fluid pressure applied to the spring is sufficient to overcome the counter-acting spring force, thereby permitting the fluid to return to the reservoir and the motor and mantle to rotate. It will further be understood that the just described anti-spin mechanism is self-resettihg.
mus when the mantle 191 has been forced to rotate in the no-load direction (the relief valve 247 has oFened) and the force applied to the mantle 191 is subsequently reduced to a level below that necessary to overoome the countervailing spring force of the valve, the spring will again cloæ the valve, once again preventing the rotation of the mantle 191 in the no-load direction.
Turning now briefly to a discussion of the lubrication system of the crusher, it is first noted that many portions of the system have already been discussed. Thus, for example the lubricating paths 83 and 127, the fact that the lubricating fluid fills the chamber within the clutch housing 131 and within the reservoir 241, and the fact that the same lubricating fluid may be utilized to urge the crusher setting indicator rod 281 upward, have already been discussed. Never-theless, it is believed appropriate at this point to briefly note the major features of the system. Initially, it is appropriate to indicate thatthe lubricating fluid is not merely injected into the crusher system where it remains in active but, rather, that the overall lubrication system, some portions of which are not illustrated, is a constantly circulating system. As a starting point, it may be noted that lubricating fluid flows into the lubrication paths 83 via the fitting 283. The 113745~

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 charnber bounded by the lower portion of seat 125, the upper portion of the shaft 81 and the radially inner portion of the eccentric 91. The lubricating fluid is further conducted along the path indicated at 127 and coats the bearing surface between the support cone bearing 129 and the support cone bearing seat 125. Clearly, therefore, the fluid also fills the chamber radially outward of the bearing 129 and the seat 125. In addition, the lubricating fluid fills the chamber within the clutch housing 131 and, as noted above, it fills the anti-spin mechanism reservoir 241. Additionally, the lubricating fluid flows into the chamber bounded by the radially outward portion of the hub 41, the lower portion of the bevel gear drive assembly 73 and the upper portion of the shaft housing member 69. The lubricating fluid is conducted from the last described chamber through a drain coupling 365 (most clearly seen in Fig. 3) by a pump (not shown) and through a filtration system (not shown) from which it may be returned to the crusher - 20 via the fitting 283. It is thus seen that the lubrication system of the instant crusher insures a constantly circulating supply of clean lubricating fluid.
It will be understood that the foregoing des-cription of the preferred embodiment of the present invention is for purposes of illustration only and that the various structural and operational features as herein disclosed are susceptible to a number of modifications and changes none of which entail any departure from the spirit and scope of the present invention as defined in the hereto appended claims.

c g/ P-''

Claims (16)

THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:

1. A fabricated upper frame for a cone crusher comprising:
a first annular member;
a first tubular member extending orthogonally relative to said first annular member, said tubular member having first and second ends and being fixedly connected, at the first end thereof, to said first annular member;
a second annular member being oriented so as to be generally parallel to, and spaced from, said first annular member, said first tubular member being fixedly connected, at the second end thereof, to said second annular member;
a third annular member being oriented to be generally parallel to, and spaced from, said second annular member; and a first plurality of circumferentially spaced ribs fixedly connected between said second and third annular members.

2. A fabricated upper frame for a cone crusher according to claim 1 further comprising a second plurality of circumferentially spaced ribs fixedly connected between said first and second annular members.

3. A fabricated upper frame for a cone crusher according to claim 2 wherein each of said second plurality of ribs has a generally U-shaped cross-sectional configuration and the open end of said U is fixedly connected to said first tubular member.

4. A fabricated upper frame for a cone crusher according to claim 1 further comprising a plurality of circumferentially spaced ribs fixedly connected between said second annular member and said first tubular member.

5. A fabricated upper frame for a cone crusher according to claim 1 further comprising a feed hopper removably coupled to said third annular member.

6. A fabricated upper frame for a cone crusher according to claim 5 further comprising a brace member, said brace member being fixedly connected to said feed hopper and removably connect-ed to said third annular member.

7. A fabricated upper frame for a cone crusher according to claim 5 wherein said feed hopper comprises:
a second tubular member; and a chute member having a cross-sectional configuration of a truncated cone, said chute member being fixedly connected at one peripheral end thereof to said second tubular member and re-movably coupled, at the other peripheral end thereof, to said third annular member.

8. A fabricated frame for a cone crusher comprising: a first annular member formed with a plurality of circumferentially spaced axially oriented holes extending therethrough;
a first tubular member extending orthogonally relative to said first annular member, said tubular member having first and second ends and being fixedly connected, at the first end thereof, to said first annular member;
a second annular member being oriented so as to be generally parallel to, and spaced from, said first annular mem-ber, said first tubular member being fixedly connected, at the second end thereof, to said second annular member;
a third annular member being oriented to be generally parallel to, and spaced from, said second annular member;
a first plurality of circumferentially spaced ribs fixedly connected between said second and third annular members;

a tubular center hub;
a fourth annular member, having a slot formed therein, oriented orthogonally relative to the longitudinal axis of said hub, the inner periphery of said fourth annular member being fixedly connected to said hub;
a second tubular member, having a slot formed therein, extending orthogonally relative to said fourth annular member, said second tubular member being fixedly connected, at one end thereof, to said fourth annular member;
a fifth annular member, formed with a plurality of cir-cumferentially spaced axially oriented holes extending there-through, oriented generally parallel to said fourth annular mem-ber, said fifth member being fixedly connected, at the inner periphery thereof, to said second tubular member;
a third tubular member, having an aperture formed there-in, oriented to extend orthogonally relative to said fifth annu-lar member, said third tubular member being fixedly connected, at one end thereof, to said fifth annular member; and a fourth tubular member oriented so that its longitudinal axis extends generally orthogonally to the longitudinal axis of said third tubular member, said fourth tubular member adapted to extend through the aperture formed in said third tubular member and the slots formed in said fourth annular member and said second tubular member, the outer periphery of said fourth tubular member being fixedly connected to the walls of said apertures and said slots, the plurality of holes formed in the first annular mem-ber being arranged for alignment with the plurality of holes form-ed in said fifth annular member, whereby said first and fifth annular members are adapted to be removably connected to one another.

9. A fabricated frame for a cone crusher according to claim 8 further comprising a second plurality of circumferentially spaced ribs fixedly connected between said first and second annu-lar members, each of said second plurality of ribs having a gen-erally U-shaped cross-sectional configuration, the open end of said U being fixedly connected to said first tubular member.

10. A fabricated frame for a cone crusher according to claim 8 further comprising a third plurality of circumferentially spaced ribs fixedly connected between said second annular member and said first tubular member.

11. A fabricated frame for a cone crusher according to claim 8 further comprising a feed hopper removably coupled to said third annular member.

12. A fabricated frame for a cone crusher according to claim 8 wherein said tubular center hub, adapted to receive a shaft, is formed with a stepped bore, the stepped bore extending longitud-inally between two points on the hub which are interjacent the ends thereof, the internal diameter of the hub at the stepped bore being greater than the internal diameter of the hub between one end thereof and the stepped bore, thereby facilitating the insertion of the shaft into the hub.

13. A fabricated frame for a cone crusher according to claim 8 further comprising a fourth plurality of circumferentially spaced ribs fixedly connected between said second and third tubu-lar members, said center hub and said fourth and fifth annular members.

14. A fabricated frame for a cone crusher according to claim 8 further comprising a fifth plurality of circumferentially spaced ribs fixedly connected between said center hub, said third tubular member and said fourth tubular member.

15. A fabricated upper frame for a cone crusher comprising:
a first annular member;
a first tubular member extending orthogonally relative to said first annular member, said first tubular member being fixedly connected, at the second end thereof, to said second annular member ;
a second annular member being oriented so as to be generally parallel to, and spaced from, said first annular member, said first tubular member being fixedly connected, at the second end thereof, to said second annular member;
a third annular member, coupled to said second annular member, being oriented to be generally parallel to, and spaced from, said second annular member; and a first plurality of circumferentially spaced ribs fixedly connected between said first and second annular members wherein each of said first plurality of ribs has a generally U-shaped cross-sectional configuration and the open end of said U is fixedly connected to said first tubular member.

16. A fabricated upper frame for a cone crusher comprising:
a first annular member;
a first tubular member extending orthogonally relative to said first annular member, said tubular member having first and second ends and being fixedly connected, at the first end thereof, to said first annular member;

a second annular member being oriented so as to be generally parallel to, and spaced from, said first annular member, said first tubular member being fixedly connected, at the second end thereof, to said second annular member;
a third annular member, coupled to said second annu-lar member, being oriented to be generally parallel to, and spaced from, said second annular member; and a brace member, adapted to be connected to a feed hopper, removeably connected to said third annular member.