CA1135231A - Mantle - Google Patents
MantleInfo
- Publication number
- CA1135231A CA1135231A CA000381740A CA381740A CA1135231A CA 1135231 A CA1135231 A CA 1135231A CA 000381740 A CA000381740 A CA 000381740A CA 381740 A CA381740 A CA 381740A CA 1135231 A CA1135231 A CA 1135231A
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- Canada
- Prior art keywords
- bearing
- head
- shaft
- crusher
- mantle
- Prior art date
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Abstract
ABSTRACT
The crusher comprises a crusher head mounted about a gyratory shaft assembly. The head comprises a mantle mounted on and secured to the shaft by a hold down cap assembly. For this purpose, the shaft is formed with a screw threaded recess, and the cap assembly comprises a screw threaded bushing secured in the recess by external threads on the bushing, which is also provided with internal threads to receive a screw threaded shank of the hold down cap assembly. The bushing is arranged preferentially to fail if the mantle is submitted to undue stress and, for this purpose, the internal threads are made less mechanically strong than the external threads so that failure preferentially takes place at the internal threads. Thus, on failure of the connec-tion between the mantle and the shaft, damage to either of the latter is avoided.
The crusher comprises a crusher head mounted about a gyratory shaft assembly. The head comprises a mantle mounted on and secured to the shaft by a hold down cap assembly. For this purpose, the shaft is formed with a screw threaded recess, and the cap assembly comprises a screw threaded bushing secured in the recess by external threads on the bushing, which is also provided with internal threads to receive a screw threaded shank of the hold down cap assembly. The bushing is arranged preferentially to fail if the mantle is submitted to undue stress and, for this purpose, the internal threads are made less mechanically strong than the external threads so that failure preferentially takes place at the internal threads. Thus, on failure of the connec-tion between the mantle and the shaft, damage to either of the latter is avoided.
Description
~l3S~3~
CO~E CR~SHER
This invention relates to new and useful improve-mentsin rock crushers and is particularly concerned with gyratory or cone-type crushers.
It is well known in the industry that gyratory or cone-type crushers operate under great structural strain in view of their required duty and the large drive forces nece-ssarily i~lparted thereto. This type of apparatus consequently is made of heavy and rugged parts. It is desired of course that for reasons of economy in manufacture as well as for opera-tion and maintenance, and furthermore for transportation onthe road and location at the site, that this type of crusher be kept as simplified as possible, low in weight, compact in size, well balanced, and quiet. Also it is desired that it have a structural connection of parts that allows maintenance in the field. Another desirable feature of such a crusher , is that it have minimum wear since the heavy and rugged parts are costly to repair or replace. Sti]l another desirable feature is that the apparatus be readily adjustable for wear or for assembly and disassembly and that the parts be securely t locked together when assembled so as to withstand the enormous shocks and stresses of crushing rock and the occasional entry of non-crushable objects.
According to the present invention and forming a primary objective thereof, a cone crusher is provided which is substantially simplified in its construction and substantially economical to manufacture and repair, which has an arrangement of parts which will withstand large structural strains and damaging forces without appreciable wear or failure, which is compact in size, well balanced and quiet, and which employs , ~3~Z31 ~ower drive means for rotatably adjusting the bo~l.
In carrying out the objectives of the invention, the connection between rotating gear input and an eccentric drive is in the form of spiral bevel gears for quiet operation and great strength and an independent coupler that allows for the precise connection that such gears require as well as ready replacement of portions of the drive assembly without disturb-ing critical gear adjustment. Means are also used to provide fluid pressure support for the gyrating head to minimize wear, and furthermore fluid pressure lift is provided for portions of the drive connection to eliminate thrust loading of the outer radial bearing caused by the weight of the inner race of said bearing and parts mounted within the inner race. An ex-terior seal is provided which due to its particular construct-ion and disposition provides effective sealing during all con-ditions of operation of the crusher. Fluid drive means are associated with the bowl of the crusher for adjusting it ro-tatably by power and for locking the bowl in a fixed position.
The invention will be better understood and additional objects and advantages will become apparent from the following description taken in connection with the accompanying drawings which illustrate preferred forms of the device.
Figure 1 is an elevational view of the present crusher, certain parts of this view being broken away to show internal parts;
Figure 2 is a vertical sectional view showing internal working parts of the crusher;
Figure 3 is an enlarged detailed sectional view of an exterior seal structure;
Figure 4 is an~enlarged, fragmentary sectional view taken on the line 4-4 of Figure 2;
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Figure 5 is a horizontal sectional view taken on the line 5-5 of Figure 2, a portion of this view being broken away and also certain parts being omitted for clarity;
Figure 6 is a perspective view of a coupler utilized in a drive connection of the apparatus;
Figure 7 is a fragmentary sectional view taken on the line 7-7 of Figure 4;
Figure 8 is an enlarged, fragmentary sectional view taken on the line 8-8 of Figure 2;
Figure 9 is an enlarged~ fragmentary sectional view taken on the line 9-9 of Figure ~;
Figure 10 is a hori~ontal, fragmentary sectional view taken on the line 10-10 of Figure 2;
Figure 11 is a fragmentary plan view of a bearing support area for the head;
Figures 12 and 13 are enlarged, fragmentary sectional views taken on the lines 12-12 and 13-13 of Figure 11, respect-ively;
Figure 14 is an enlarged, fragmentary, foreshortened sectional view taken on the line 14-14 of Figure l;
Figure 15 is an enlarged detail view of a portion of Figure 14;
Figure 16 is a lragmentary elevational view tak~.l on the line 16-16 of Figure l;
Figure 17 is a fragmentary sectional view taken on the line 17-17 of Figure 16;
Figure 18 is a fragmentary elevational view showing a re].ief system operable upon the entry of non-crushable objects into the crusher;
Figure 19 is a fragmentary plan view taken on the line 19-19 of Figure 18;
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~ igurlc 211 i d f C.lg~llenl:ar'y pkln v:ie~ taken on the line '20-20 of Figure 14;
Figure 21 is a fragmentary elevational view taken on the line 21-21 of Figure 20;
Figure 22 is an enlarged, fragmentary sectional view -taken on -the line 22-22 of Figure 21;
Figure 23 is a view taken similar to Figure 14 but show-ing a modified structural arrangement for power ro-tation of the bowl;
Figure 2l~ is an enlarged, fragmen-tary sectional view taken on the line 24-24 of Figure 23i Figure 25 is a fragmentary eleva-tional view taken on the line 25-25 of Figure 23;
Figure 26 (on the sheet bearing Figure 20) is .1 fragmen-tary plan view taken on the line 26-26 of Figure 23;
Figure 27 (on the shee-t bearing Figures 2 and 3) is a fragmentary sec~ional view showing a modified bearing suppor-t for the crushing head; and Figure 28 (on the sheet bearing Figures 11, 12 and 13) is .' a view similar to Figure 2 but showing modified eccentric drive stnucture.
With par-ticular reference -to -the d:rawings and first to Figures 1 and 14, the crusher cor~lprises a lower circular body frame portion 25 reinforced by an upper integral annular ring 26 and a ~Lower in-tegral annular ring 27. The crusher is bolted or other-wise secured to ., suitable support 2~. Upright reinforcing webs 29 are welded to -the ex-terior of body por-tion 25 be-tween upper reinforcing rings 26 and 27. An oil reservoir 30 is formed a~ound the lower outer periphery of body portion 25 and flange 27 to 3~ provide good oil capaci-ty for lubrication of the crusher. This Mounting arrangement of reservoir 30 uses the body portion 25 as a hea-t sink.
The main body portiorl oE the crusher includes an inter-3~
nal centrally located ~ ~shaped frame portion 31, Figure 2,integrated with the circular frame portion by three or more I-beam type struts 32. The upper edge of frame portion 31 has a head support or thrust member 34 in the form of a ring re-movably attached thereto, and this head support has a spherical or dished upper bearing surface 35 which is engaged by a bottom arcuate surEace 36 on a crushing head 37 in a manner to be descri-bed more fully hereinafter. ~lead 37 supports mantle 38 on machined contact surfaces and by the medium of a filler layer 39 therebetween. A hold-down cap assembly 40 to be later described holds the mantle removably on the head.
With particular reference to Figures 1 and 1~, head 37 cooperates with an annular bowl 41 having a hollow frusto-conical surface 42 and having an inturned flange 43 below its upper edge which supports a liner 44 by means of eye-bolts 45 in a conventional manner. A hopper portion 46 is removably attached to the bowl 41 and directs rocks to be crushed into the area between the gyrating head 37 and the liner 44. Rock that has been crushed falls down around the exterior of ~rame 20- portion 31 and is carried away by suitable conveyor means not showm.
Input drive for the crusher comprises a shaft 50, Fig-ures 1 and 2, having an outward projecting end for securement to a drive sheave 51 rotated by suitable power apparatus not sho~m. The shaft 50 extends through an inwardly projecting housing 52 within a larger housing 52a. Sha~t 50 is supported by bearings 54 and housing 52 has an outside flange 53 abutted against the outer surface of housing 52a. This shaft and bear-ing assembly is installed and removed as a unit and housing 52 can be adjusted longi~udinally if necessary such as by shi~ing.
The inner end of shaft 50 has a bevel pinion gear 55 keyed or 3 ~ ~
otherwise secured thereto, and this pinion gear has meshing engagement with an annular bevel gear 56, also seen in Figure 4, removably secured to a flange 58 integral with a depending shaft 59 having journaled engagement in an annular upright housing 60 removably secured to the bottom of central frame portion 31. Journaled engagement of shaft 59 in the housing 60 is by upper and lower bearings 62.
Shaft 59 stabilizes flange 58 which drives an eccentric member 68 by means of an intermediate coupler 69, Figures 2 and 4-7. This coupler has a diametral groove 70 in its bottom sur-face and a diametral groove 71 in its top surface extending at right angles to the groove 70. A pair of spaced lugs or keys ~2 are releasably secured, as by screws 73, to the upper sur-face of flange 58 and slidably fit in the groove 70 of the coup-ler. Likewise, a pair of spaced lugs or keys 74 are releasably ; secured, as by screws 75, to the bottom surface of eccentric member 68 and slidably fit in grooves 71. Each of the lugs 72 and 74 fits in a recess 76 in the part to which it has screw connection.
The connection provided~by the coupler 69 thus comprises an independent connection between the drive gear 56 and the ; eccentric member 68. This independent connection, rather than comprising a direct connection between the gear and the eccen-tric member, accomplishes a first advantage of providing precise gear fit adjustment between the pinion gear 55 and the bevel gear 56. That is, such precise engagement can readily be accom-plis~ed if necessary by installing shims, not shown, between the flange of the bearing housing 52 and the housing 52a for horizontal adjustment and between the flange 58 and the gear 56 for vertical adjustment. Another advantage of the coupler 69 is that said coupler is of ~slightly less thickness than the spac- -~ 3~
ing between the flange 58 and eccentric member 68 and such clear-ance acco~nodates any misalignment and prevents vertical binding Furthermore, since the lugs 72 and 74 fit in recesses 76 in the parts to which they have screwed attachment, the rotating torque is taken directly by the coupler and the lugs and a shearing force is not put on the screws 73 and 75 The coupler 69 also has the advantage of simplifying accurate gear adjustment and replacement of associated parts in the field. Further yet, the coupler arrangement allows spiral bevel gears to be used, such type of gears having the advantage of being stronger and quieter than straight teeth gears.
A heavy shaft 80, Figure 2, is fitted into an axial bore 81 in the head 37 and has association, to be described, with the eccentric member 68 for producing the gyrating action of the head.
The hold-down cap assembly 40, which includes a torch ring 40a, has releasable engagement with the top end of the shaft for holding the mantle 38 in place. This cap is of conventional construction - -except for its threaded connection with the shaft 80. In this re-gard, the shaft has a threaded recess 82 arranged to receive a threaded bushing 83 also having internal threads for receiving a threaded shank 40b of cap 40. Since the outer threads on bushing 83 are stronger than the internal threads of said bushing because o~ their larger size, any failure of connection between the cap and the shaft will occur in the inner threads, thus eliminating damage to the shaft and usually only requiring a replacement of the bushing.
With particular reference ~o Figures 2, 8 and 10, eccen-tric member 68 has an integral upstanding housing 84 with the eccentric shape as best seen in Figure 10. This housing is jour-naled within a large self-aligning roller bearing assembly 85 seating at its bottom end on a shoulder 86 on frame 31 and on a shoulder 87 on the eccentric member 68. A sleeve 88 with an outer wall surface which is tapered inwardly toward the bottom is press t,~ .
fitted to the outer race of the bearing 85 and has wedging en-gagement in an upper portion 89 of the frame 31. Portion 8~
has a matching taper with the outer surface of sleeve $8. Thè
tapered sleeve 88 provides a means to press fit the outer race in place, such being necessary with the type of loading im-posed, and also this sleeve is easily removable which makes re-placement of the bearing 85 easy. A retaining ring 90 is re-leasably secured to a top flange of tapered sleeve 88 to pre-vent the bearing 85 from creeping upwardly. Retaining ring 90 may require shimming if the top face of sleeve 88 locates be-low the top face of the bearing 85. A lock nut 93 holds the eccentric member 68 from dropping out of bearing 85.
The bore housing 84 accommodates a cylindrical roller bearing assembly 95 whose inner race has a press fit on the shaft 80. A shoulder spacer 96 abuts against head 37 and has a slight clearance with a tapered portion 97 of the shaft 80. A
.retaining plate 98 bolts to the bottom of shaft 80 to properly position the inner race of bearing assembly 95 in place.
~ As best seen in Figure 2, the axis of shaft 80, de-signated by the nu~eral 99, is offset ~rom the axis 100 of the outer or-camming surface of the eccentric housing 84, and further-more-the inner bearing 95 and shaft 80 have tilted engagement within the inner bore of housing 94 by a selected angled bore of said housing whereby the axes 99 and 100 are offset at the bottom but meet at a vertex V at an upper portion of the crusher. ~pon rotation of the eccentric member 68, gyrating actions of the head 37, as designated by reference numeral 37a in Figure l, are accomplished.
The eccéntric member 68 has an extension 104 at one side-, Figures 2 and 5, which serves as a counterweight. In addi-tion, a counterweight 105, Figures 2 and 8, is releasably secured t~ the top edge of the housing 84 in an area approximately above the counterweight 104. Counterweight 105 also serves as ~~_ o ~ 3~3 ~
a retainer for the outer race of bearing 95. These counter-weights serve to balance the cen~rifugal force of the gyrating cone assembly so the entire crusher sits quietly on its founda-tion without imposin~ destructive shaking motions to said foundation.
As stated hereinbefore, the bearing surfaces for the head 37 in its gyratory crushing movements comprises the co-operating surface 35 on the head support 34 and surface 36 on the head 37. Such surfaces take massive thrust forces that can crush through hydrodynamic oil films and thus are subject to damage.
In order to provide maximum bearing life, however, and with re-~erence to Figures 2 and 11-13, surface 35 has an annular recess 108 which receives a plurality o~ arcuate segments 109 of bronze ; bearing ~laterial or a non-metallic low coefficient of friction material such as Teflon~Delrin~Nylatron~or other suitable material. Oil under pressure is admitted to the bearing surface between head 37 and inserts 109 through passageways 110 in the frame 34. A passageway leads-to each segment and`opens into-its bearing surface-, a combination duct and locating pin lll that is sealed against oil leakage at its outer diameter by O-rings. An enlarged recess 112 is formed-ln segments lO9 and has radiating grooves 113 for efficient distribution of the lubricating oil to the full surface OL the segments. The discharge of oil from the seg~ents 109 is through outlet passageways 114 in the head support 34 and in the segments 109, the passageways 114 communicating with end spaces 115 between the segments. The ends of segments 109 throughout a greater portion of their length ha~e an inward taper 116 for efficient pickup of oil to be discharged from the lubricated bearing surface.
The longitudinal edges of the segments lO9 have oil seals 117 of a suitable type ~Jhich will withstand high pressure and re-tain the lubricating oil between the two seals. The outer and inner edges of segments lO9 closely abut each other to reduce oil _ g_ ~3~
escaping under seals 117. A third seal 117a is disposed out-wardly from the outermost seal and is arranged to prevent inlet of dust and to wipe any escaped oil into an annular groov~
118 which is provided in the frame 34 and which com~unicates witn the drain 114. Drain 114 empties into the space above the bearings 85 and 95, Figure 2.
The inlet of oil through passageways 110 is introduced at high pressure and more particularly at a pressure which is greater per square inch than any possible working pressure on the head 37. Thus, a hydrostatic support is provided between the head 37 and the head support 34 to maintain a layer of lubri-cating oil between the surfaces and substantially eliminate any metal to metal contact under the most severe conditions, thereby keeping friction to the lowest possible value and mini-mizing wear. When attempting to re-start a crusher that has stalled due to overload, a-crusher without this hydrostatic fea-ture will 'h?ve this bearing surface in tight metal to metal contact, and- starting would have high-friction and bearing stresses. With this hydrostatic system, oil pressure will lift the cone head like a hydraulic jack. Metal bearing surfacesare separated before the crusher is started by suitable control means, and starting is easier and free of bearing damage. It is preferred that each segment have its own or individual pumping pressure to provide ; uniform and constant pressure support around the head, thus eli-minating migration of oil pressure to lower pressure working areas of the head. The oscillating surfaces between the two mem-bers spreads the lubricating oil in an efficient manner and in addition the head 34 tends to rotate slowly in a direction opposite to the rotation of the eccentric member 68. The resulting motion is a wave patiern on the bearing to provide a well lubricated, long wearing support of the head on the base frame.
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23~
With ~efe~ence to ~igures 18 arld lg, a purr,p assembly is provided for the plurali-ty of se~ments 109 and cornprises individual pumps 119 secured on the crusher frame and disposed around a common gear case 120. Driving operation of the gear case is by motor 121 and connecting shaft 122. Individual pumps 119 are connected to respective segments 109 for reasons pointed out hereinbefore by individual conduits and passageways 123 and have intake from the oil reservoir 30 by sui-table condu:i-ts. One or more pumps 119 can be included in the pumping assembly for lubricating other bearings in Ln -thc assembly. An alternative to multiple pumps is one purnp followed by a series of flow dividers that are capable of maintaining even flow in two directions despi-te pressure differentials.
It is to be understood that although the use cf segmental inserts 109 are disclosed in the preferred embodiment, such inserts may be omitted and the hydrostatic pressure provided directly be-tween the metal surfaces of the head and *rame.
The combined weigh-ts of eccentric member 68, the inner bearing 95, the rollers, cage, and inner race of bearing 85, and , o-ther associated members attached to 68, are considerable and 20 would impose a significant -thrust load on the bearings 85 if not neutralized by some means. In this regard, and with reference par-ticularly -to Figure 4, a fluid pressure passageway 125 leads upwardly through the shaft 59 and has pr-essured supply through a conduit 126 fl~m suitable pump means such as a pump 119.
Passageway 125 eorrlnlurlicates with the interior of a cylinder 127 extending through a central opening 128 itl the coupler 69 and having a piston 129 therein. The upper end of this pis-ton has - an annular projection 130 which abu-ts against the lower surface of eccentric member 68. Pis-ton 129 has a preset relie* valve '(1 l3l therein, dnll t~lC ou-tlct ~rom this valve co~mul~icates with a port 132, also seerl in Figure 2, which leads -through eccentric member 68 wherel>y o:il passing through such port can flow acrosS
tllc upper suria(e ()l I lle eecQI~lri( Inc~ er 6B and ., . ,, . . . . .. , _ _ _ . .. . _ _ _ _ . . ... . .
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lubricate bearings 95. Piston 130 under the action of ~luid pressure will bear the weight of the eccentric member 68 and other parts, the relief valve 131 opening at pressures ~ -as near eq~lal as possible to the desired supporting pressure before admitting lubricating oil to the bearings 95 and other lubricated areas, to be described.
In adclition, a hollow piston 135 operates over a hub 136 formed in a bottom plate 137 releasably attached to the frame 31. The piston 135 is urged upwardly by a spring 138 into abutment with a hardened face bearing 139 having an O-ring seal therein. The area of hub 136 is greater than the face con-tac~ of piston 135 on the bearing 139 and thus oil pressure in passageway 125 which extends through all these members will hold the piston against the bearing and override the same oil pres-sure trying to separate them. The result is that piston 135 prodllces an upward lifting force on the shaft 59 sufficient to pre~ent excessive leakage from oil pressure in conduit 125.
; Suitable means, not sh'own, are associated'witX piston 135-'to prevent it from spinning on hub 136.
As stated, lubrication oil moving upwardly through port ; 132 will lubricate the inner bearing 95. The forced movement of such oil u?wardly will flow or be-thrown over into the area of the outer bearing 85, Figure 2, and also lubricate it. In addition, it is apparent that oil draining from the bearing surfaces 35 and 36 between the head and the frame will also provide some lubrication. Also, several passageways 142 lead downwardly from the area above the bearing 85 and empty into the interior of frame 31, and as shown one of such passageways empties into housing 52a above shaft housing 52. Oil draining through this latter passageway 142 is directed through a port 143 in the housing 52 by a baffle 144 for lubricating the bear-ings 54 Oil also drains down through bearing 85 into the bottom ~13S~3~
~of cup-shaped frame 31 and an oil level 145 is maintained for lubricating the gears. Housing 52a has co~-mnunication with the interior of frame 31 to serve as an additional reservoir, as well as to provide a cooling or heating area for the oil Because there is a creep fit between housing 84 and the inner race of bearing 85, it is desired that the engaging sur-faces between such inner race and the housing 84 be lubricated.
For this purpose and with reference to Figures 2, 8 and 9, a shield 148 is releasably secured to the upper edge of housing 84 and extends part way therearound. This shield is spaced a short distance above the top of the h~using 84 and is arranged to catch oil thereunder and direct it down through several passageways 149 co~unicating with an arcuate groove 150 in the outer surface of housing 84 and in the lock nut 93. By means of this groove, oil is distributed around for additional lubri-cation to bearing 85 so centrifugal force does not throw all the emerging oil beyond bearing 85. Lock nut 93 has several - passageways 151 leading outwardly from the groove 150 for direct-ing said oil to the bearing 85. Also, an auxiliary passageway 152 leads downwardly from passageway 149 and provides oil seepage between the inner race of bearing ~5 and the outer surface of housing 84.
-~ With reference to Figure 2, a frusto-conical seal 156 is secured between a ring 157 releasabl~ secured in a peripheral notch 158 in the bottom edge of a depending flange 159 of the head 37. T~e other end of the seal is connected to a ring 160 supported on a peripheral shoulder 161 in the head support 34.
Ring 160 is free to rotate relative to the support 34 and has bearing support in the groove 161 by bearing layers 162 of suita-` 30 ble bearing material such as non-metallic low coefficient of friction material. Seal 156 is formed of flexible and stretch-able material which is airtight and oil and ozone resistant.
o '.
~Z~l One acceptab]e material for this pllrpose is polyurethan2.
Importantly, this seal in its frusto-conical shape is directed substantially toward the vertex V whereby such seal will o?erate efficiently through all normal operating conditions of the head 37. That is, this seal due to its angular disposition will efficiently follow the gyratory movements of the head with the least amount of stretching and at the same time can rotate ~ith the head by movement of the ring 160 on the shoulder 161 and bearing 162. This seal will protect the internal workings of the crusher from the entrance oE dust, although in the remote circll;nstances that such seal should fail, the outer seal 117a of bearing surfaces 35 and 36, best seen in ~igure 12, will keep dust from entering the bearing surfaces and interior of the machine. The upper end of ring 160 is tapered downwardly at 163 toward the center to drain oil which may have escaped into such area back into the drain 114. An inclined port 164 leads from such iapered surface 163 to the drain 114.
With reference to Figure 3, the ring 157-has a passage-way 165 therethrough for draining oil through the seal wnich may have escaped into the lower area of the seal, such oil merely dripping out to the exterior of the apparatus. A ~ilter 166 is mounted in the ring 157 across the pa-ssageway 165 to prevent the entrance of dust upwardly through the passageway.
A bowl support 170, Figures 1 and 14 (also seen in a modification view of Figure 23) has an upper peaked portion 171 and a lower notched portion 172 arranged to seat on the annular reinforcing ring 26 and to extend down in a pressed fi~ into the top portion of body frame portion 25. Bearing liners 173 of suitable material such as l~icarta~are bonded to the ring 26 and machined portion of frame 25. Bowl support 17~ can slip relative to the base if a sufficient and generally abnormal torque is present and such comprises an important advantage of the instant apparatus because it relieves undersirable torque in the frame.
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It is desired t'nat the bowl support 170, although being able to slip relative to the frame, be held against vertical movement off the frame, and for this purpose several clamps 175, Figure 16 (and also Figure 23) are bolted to the ring 26 and have finger projection into a peripheral groove 176 in the support 170.
Seated on the bowl support 170 is an annular frame or large nut 179 having an outwardly projecting flange 180 and also having an inYerted V-shaped groove 181 in its bottom sur- -ace for seating engagement on the support 170. Nut 179 has internal threads 182 having meshing engagement with exter-nal threads 183 on the bowl 41.
During hard crushing, there is a tendency for the bowls of cone crushers to lift slightly or float on the frame support. This action creates enormous torques that want to drive the bowl circularly relative to the supports. In order to prevent such rotation, several depending stops 186 on the nut 179, Figures 1 and 16, abut against upstanding companion stops 187 on the--ring 26. Rotation is thus prevented between the nut 179 and the base frame in the one direction, but as stated, the bowl support 170 can slip if forces are great enough, The engaging faces of the stops 186, 187 are angled slightly to allow tneir top edges to miss each other when closing back together from a separation. These stops may be made to face in opposite directions than that shown for reverse rotation of the input shaft, or if desired stops that work both ways can be used.
The floating movement of the nut 179 on the bowl support 170 is controlled by a fluid operated hold-down mechanism compri-sing a plurality of fluid operated cylinders 190, Figures 16-l9, spaced around the exterior of the crusher frame and associated with a tram? iron relief system. The upper end of each cylinder 190 is bolted to the ring 26, such c-~linders have pis~ons l91 engage-a ~35'~
able with thrust rods 192 extending in sealed engagement through the lo~Jer end of the cylinders into abutment at their lower ends against beams 193. The ends of the rods 192 are rounded and engage rounded portions of the pistons 191 and beams 193 for pivotal adjustment. Each beam 193 pivotally supports a pair of eye nuts 194 at opposite ends thereof and these eye nuts have vertical grooved guided engagement with vertical guides 195 secured to the webs 29. A pair of vertical rods 196 have threaded engagement at their lower ends with respective eye nuts 194, and these rods pass freely through ring 26 and the flange 180 of nut 179. The upper end of rods 196 receive hold-down nuts 197 and spring washers 198 between the nuts and the flange 180. Thrust rods 192 are held tightly in place between their pistons 191 and beams 193 by the spring washers 198 and by the tramp iron relief system now to be descri-bed.
Manifold sections 200 are coImected to upper portions of two or more of adjacent ones of relief cylinders 190 to-provide co~munication of these sets of cylinders with each other. One of the manifolds communicates with a pressure switch 201 by a conduit 202. Switch ~Ol has electrical connection by wires 203 with an electric motor 204. Switch 201 controls operation of motor 204 and will start the motor upon a selected lowering of pressure in manifold 200, as will be more apparent hereinafter.
Motor 20~ drives a hydraulic pump 205 connected on its input side to a pair of accumulators 206 by a conduit 207. Accumu-lators 206 are in communication with each other by a manifold 208. A third manifold 209 extends around the machine adjacent to manifold 208 and has communication with all the manifolds 200 by vertical connecting conduits 210.
A valve assembly 212 is connected to manifolds 208 and 209 and has a valve chamber 213 associated with manifold 208 1~3~23~
and a valve cha~ber 214 associ~ted wi~h manifold ~09. A sprin~
loaded plun~er valve 215 operates between valve chambers 213 and 214 and is arranged to control ~luid flow ~rom charnber 214 to chamber 213 in one direction, the latter chamber being en-larged at 213a around the plunger to allow free passage of fluid between the two accumulators 206. Valve 215 is selectively pre-loaded by a spring assembly 216, preferably comprising a stack of spring washers, thrusting agai~t an auxiliary plunger 217 having a ball and socket engagement 218 with plunger 215. Ball and socket connection 218 preve~ts any binding of plunger 215.
A pair of ball check valves 220 as well as valve 215 stops fluid flow under normal conditions from chamber 214 to cnamber 213, the check valves 220 being held in operative position ; by retaining pins 221. A conduit 222 leads from the outlet of pump 205 to chamber 214 of valve assembly 212, this conduit ;
having a check valve 223 therein to prevent oil from bleeding back into the pump. Chamber 214 has a manually operable relief valve 224 to drain the pressure from the system.
The relief system is set up ~or operation as follows;
The cylinders 190 and-their-manifolds 200 and 209-, as well as chamber 214 in valve assembly 212, are pressurized at a specific prPssure, Ior example, 2500 PSI, this pressure comprising a de-sired-hold-down--force for illustration purpose. The lower chamber 213 of valve assembly 212 as well as the accumulators and-manifold~208 are pressurized at a pressure a ~ew hundred pounds lower than the pressure in chamber 214 and its associated parts, ~or example, 2100 PSI. The accumulators 206 are initially charged to approximately 1800 PSI with nitrogen gas. Oil is then pumped into the accumulator system to raise the pressure to the desired 2100 PSI. This builds up an ample reservoir of oil for pump 205 to keep chamber 214 suitably charged as will be descri-bed. The pressure in the accumulators will vary according to temperature but the pressure in chamber 214 will be substantially o 3~3~
.constant. Spring 216 is pre-loaded to allow plunger valve 21~
to open at a higher pressure than that which exists in chamber 21~, for example, 2750 PSI. The pressure switch 201 is arranged to energize the pump motor 204 when the pressure drops a slight amount below the pressure in the relief cylinders, for example, 2475 PSI. In normal operation, some slight up and down move-ment of the bowl 41 and nut 179 will exist. This slight move-ment will be absorbed by the springs 198. Such spring action prevents damaging fluttering movement of the pistons 191 in their cylinders 190.
~owever, when a non-crushable object such as a piece of "tramp iron" enters the crusher, the bowl 41 and nut 179 raise more than normal as the cone-shaped head 37 presses against the obje~t. The pistons 191 in the relief cylinders 190 in that particlllar section of the relief system rise and hydraulic fluid flows ;:hrough manifolds 200 and 209 into valve chamber 214 and push the plun~er 215 open. Fluid then flows into chamber 213 of valve assembly--212 to-provide relief ln-the cylinders-l90- -and thus in the hold-down function. The accumulators 206 absorb fluid entering valve chamber 213 and manifold 208. As the cone gyrates away Lrom the object, the fluid returns from chamber 213 to chamber 214 through ball check valves 220. This action repeats until the object has cleared the crusher and as is appar-ent the pressure in the two valve chambers 213 and 214 wi.ll be substantially the same. As soon as the pressure in manifold 200 gets below a selected value, namely 2475 PSI in this illustration, switch 201 starts motor 204 for restoring normal pressure to valve chamber 214 and of course the relief cylinders 190. In this arrangement, the pump only has to raise the pressure a small amount, for example, from the lowered pressure to the 2500 PSI
normal. Such eliminates the necessity of the pump having to raise the pressure back up from zero.
3 ~ ~3~
It is necessary to firmly jam or lock the thread engagement between bowl 41 and t.he nut 179 to maintain desired crusher adjustment and to resist destructive movement during crushing operations and when violent inertial action occurs from non-crushable objects passing through the crusher. For this purpose, an annular jam nut 230, Figure 14, seats on the top edge of nut 179 and threadedly engages the threads 1~3 of the bowl. A non-metallic low coeff:icient of friction bearing washer 231, also seen in Figure 15, is disposed between the jam nut 230 and the nut 179. With particular reference to Figure 15, thread liners 232 which may also be constructed of a non- i metallic low coefficient of friction bearing material are secured between the threads 182 and 183. Preferably, these liners are secured to the threads 182 on the nut 179. The threads and liners are dimensioned and arranged such that those :~ on the bottom surfaces of threads 182 fill the space between the - threads 182 and 183. These threads take the upward thrust of - bowl 41 during crushing operatlons. The liners on the upwardly facing surface of threads 182 have clearance with threads 183 and merely serve as bearing surfaces when the crusher is being adjusted. A liner 233 may also be provided be~ween an upwardly facing surface of one or more threads of jam nut 230 and threads 183. The liners 232 and 233 reduce the unlocki.ng force required to release nuts 179 and 230 and provide assist in the adjus~ent of che crusher while crushing by eliminating metal to metal con-tact and a much reduced coeffici2nt of friction. These liners also prevent seizing of the threads by galling or corrosion.
An upright sleeve 235 is secured, as by welding, to the outer peripheral surface of jam nut 230 with portions there-of projecting above and below the jam nut. Attached to theinner surface of the lower projecting portion of sleeve 235 are one or more depending arms 236) Figures l and 16, pivotally o 3~
.connected to one end of a ~luid operated cylinder 237. The ' other end of cylinder 237 is pivotally anchored to a post 238 integrated with the ~lange 180 of nut 179. The working move-ment of the fluid o?erated cylinders 237 is such as to ~ully release the jam nut 230 in one direction of movement and to fully lock the jam nut in the other direction of movement. Two of the cylinder assemblies 237 are disposed in diametrical re-lation on the machine and are used to balance the torque drive.
The fluid operated cylinders 237 are selectively disposed and the thread arrange~ent is such that the cylinders utilize a pus~ing movement of their pistons to unlock the jam nut 230, thus utilizing the greater power of the pistons as compared to their pulling ?ower to release the break-out torque and friction re~ d which is greater than the locking friction. Because it i: r,landatory to unlock the system before adjustment can be made, ~e cylinders must have enough thrust to accomplish this ; unlo.~lng and rotating function. Means are provided for the power rotaijS~n of bowl 41 for functions of its installation, removal, or adjustment, and for tnis purpose, an annular angular housing 242, Figures 1 and 14, is bolted to the top edge of the bowl 41 and made dust tight therewith by an-O-ring seal 241. Housin~
242 extends downwardly in partial overlapping relation with the sleeve 235, and a combination bearing and dust seal 243 is dis-posed between the overlapping portions to allow a sealed bear-ing rotation between these parts. The exterior of the housing has a plurality of evenly spaced vertical projections or lugs 244.
One or more truss-like members 246, Figures 14 and 20-22, have an inte~ral bottom plate 247 bolted to brackets 248 welded to the nut 179. Two fluid operated cylinders 249 are pivotally anchored to end posts 250 and are pivotally connect-ed at their other ends to respective lever arms 252 integral with upright sleeves 253 pivotal on shafts 254 supported in the truss - member 246. The upper ends of sleeves 253 have a lever arm 256 -20.
which is pivotally connected to one end o a pawl 257 having a hook end 258 arrar.ged for pulling engagement with projections 244. Pawls 257 are urged rotatably toward the housing 242 into engage~ent with projections 244 by means of torsion springs 259 contained on a depending extension 260 of the pivot supp~rt for the pawl.
The ends of the pawls 257 opposite from the hook end have an integral extension 263 projecting under the lever arm 256 and terminating in a second hook 264. These hooks are associated with stops 265 on the undersurface of arms 256. The arrangement is such that upon retracted movement of the fluid operated cylinders 249 to a point where the arms 256 and pawls form approximately a straight line, the hooks 264 engage stops 265 to stop the action of the springs 25~ on their pawls 257, whereby continued retracting movement of the cylinders causes the pawls to swing clear of lugs 2k4.
In the operation of the power rotating means for the bowl 41, one cylinder 249 will drive while the other one re-tracts whereby upon repeated operations, the bowl can be ratcheted in the direction desired. The controls for operating the cylinders 249 are not shown but their operation is readily accomplished by conventional valving either under manual control or by auto-matic control. Rotation of the bowl for adjustment vertically or for releasing it after crusher use will take place of course only after release of the jam nut 202 which will again be tight-ened when rotation of the bowl has been completed.
A modified form of power rotative adjust~ent of the bowl is shown in Figures 23-26. Tnis embodiment also shows a slightly different bowl and jam nut construction wherein the jam nut 230' has a sleeve 235' bolted to the upper surface thereof which projects upwardly in close association to the threads-183 of the bowl. An angular housing 242' on the bowl overlaps a portion of the sleeve 235'; a combination seal and bearing t~ -21-~ 3~
243' being provided betwf en the overlapping portions. Evenly ' spaced projections or lugs 244' are provided on the bowl.
A vertical plate 268 is bolted to brackets 269 welded to the nut 179, and such plate supports integral posts 270 at opposite ends thereof. One of the ends of a pair of fluid operated cylinders 271 is connected to the respective posts and the ends of the piston rods are pivotally connected to notched ends 272 OI a single pawl or slide block 274. Pawl 274 has a centrally located inner edge notch 275 and a pair of shallow end notches 276. As will be more apparent hereinafter, the pawl 274 is arranged to drive the bowl in either direction, and as best seen in Figure 24 the notches 275 and 276 are arranged such that the pawl will engage two of the projections 244' at a time for driving in either direction. A cap screw ; 277 passes through an elongated guide slot 278 in a curved ; guide plate 280 and is threadedly engaged with the pawl 274.
Cap screw 277 is adjusted with sufficient clearance so as to have slidable guided movement of pawl 274 against plate 280.
A cap plate 281 is bolted to the top of pawl-274 and overlaps the plate 280 to shield the slide surface from dust and assist in the stabilization of pawl 274.
A pair of spaced standards 283 are secured integrally to the nut 179 and pivotally support at their upper ends a lever arm assembly 284 having an upright body portion 285 secured integrally to the bottom of the pawl supporting plate 280. A toggle assembly 286 is pivotally supported at the lower ends of the standards 283> and such toggle assembly is pivotally connected to the upper lever arm assembly 284 by-two toggle links 287. An upright fluid operated cylinder 289 is pivotally support-ed at its lower end on a bifurcated arm 288 integral with toggleassembly 286. The upper end o~ cylinder 289 is pivotally connected to lever arm assembly 284. As seen in ~ull and broken lines in Figure 23 such cyli~der is arranged to pivot the upper 1~35~3~L
lever arrn assembly and the toggle assembly to e~tend or closethe pawl 274. Tne toggle links have stops 292 which limit overcenter movement in an outward direction.
The two fluid operated cylinders 271 operate in unison, namely, they assist each other in both directions of operation.
When it is desired to turn the bowl of the crusher, fluid operated cylinder 289 is first extended to place the pawl 274 in engage- --ment with projections 244'. Jam nut 230' is then unlocked, the cylinders 271 are driven in the desired direction and upon com-pletion of their travel, the cylinder 289 is retracted to release the pawl 274. The cylinders 271 are then operated in the opposite direction to move to a new drive position at which time the cylinder 289 again moves the pawl inwardly. This procedure is repeated to provide the desired rotation. When the desired ro-tation is made and a crllshing operation is to take place, the jam nut 230' is tightened by means of its fluid operated cylinder.
The pawl construction of the embodiment of Figure 23 has the advantage that the bowl cannot overrun when adjusting since the pawl will catch and hold any such over-running rotation. Also, since the two fluid operated cylinders work together, half as large a cylinder area is required as compared to whereone fluid operated cylinder does the work. Either adjusting system of Figure 20 or Figure 26 will work with either housing 242 or 242', Referring to Figure 27, a modified bearing support bet~een the cone-shaped head 37' and the head sup?ort 34' is illustrated. In this embodiment, a bearing insert 294 is set in a recess 295 in the head 37' and has a spherical botto~ surface engaging the dished supporting surface of head support 34`.
Insert 294 may be replaced as necessary.
P~eferring to Figure 28, a modified form of eccentric drive ls shown for the main upper shaft 80'. In this modifica-tion, the eccentric member is a triple race bearing having an eccentric middle race ~4a' and-is similarly driven from below 3;~Z3~
as in the fi~st embodi~lent. It also employs a counterwei~ht portion 104'. The middle race ~4a' has a driving flange 68' bolted to its lower face and carries a counterweight 105' at its upper face. Middle race 84a' is journaled bet~7een an inner set ff of rollers and an outer set of rollers. Its outer surface thus coMprises the inn~r race for a large self-aligning roller bearing 85' engageable with an outer race 84b'. Outer race ~4b' seats on the shoulder 86 of the frame 31. The middle race 84a' forms the outer race of roller bearings 95' whose inner race 95a' 10 has a press fit on the shaft 80'. A shoulder spacer 96' and a retaining plate 98' hold the inner race 95' in place. As in the first embodiment, a tapered sleeve 88' is press fitted within the frame 31, and a retaining plate-90' is bolted to the top of this sleeve to hold the outer race 84b' in place.
The eccentric and drive arrangement of the embodiment of Figure 28 is similar to that illustrated in Figure 2 with the exception that the eccentric midrace 84a' is utilized also as bearing races on opposite surfaces thereof, thus minimizing the number of parts necessary in this radial bearing area and provi- ¦
20 ding a more-compact design.
According to the present invention, a gyrating or cone-type crusher is provided which is extremely efficient in operation and which is relatively simplified and inexpensive to manufacture. The parts operate efficiently with a minimum of wear and are arranged for easy replacement. In addition, the inner parts are effectively sealed against the inlet of dust or foreign particles to further prolong the working life of the parts.
Further yet, means are provided to minimize damaging strains in the various parts and also, power adjustment of the bowl facilitates 30 operation of the crusher by a single person.
It is to be understood that the form of my invention herein shown and described are to be taken as preferred examples ~ -24-~13~31 " ~ ~.
of the same and that various changes in the shape, size and arran~ement of parts may be resorted to without departir,g from the spirit of my invention, or the scope of the subjoined claims.
~ - .
,
CO~E CR~SHER
This invention relates to new and useful improve-mentsin rock crushers and is particularly concerned with gyratory or cone-type crushers.
It is well known in the industry that gyratory or cone-type crushers operate under great structural strain in view of their required duty and the large drive forces nece-ssarily i~lparted thereto. This type of apparatus consequently is made of heavy and rugged parts. It is desired of course that for reasons of economy in manufacture as well as for opera-tion and maintenance, and furthermore for transportation onthe road and location at the site, that this type of crusher be kept as simplified as possible, low in weight, compact in size, well balanced, and quiet. Also it is desired that it have a structural connection of parts that allows maintenance in the field. Another desirable feature of such a crusher , is that it have minimum wear since the heavy and rugged parts are costly to repair or replace. Sti]l another desirable feature is that the apparatus be readily adjustable for wear or for assembly and disassembly and that the parts be securely t locked together when assembled so as to withstand the enormous shocks and stresses of crushing rock and the occasional entry of non-crushable objects.
According to the present invention and forming a primary objective thereof, a cone crusher is provided which is substantially simplified in its construction and substantially economical to manufacture and repair, which has an arrangement of parts which will withstand large structural strains and damaging forces without appreciable wear or failure, which is compact in size, well balanced and quiet, and which employs , ~3~Z31 ~ower drive means for rotatably adjusting the bo~l.
In carrying out the objectives of the invention, the connection between rotating gear input and an eccentric drive is in the form of spiral bevel gears for quiet operation and great strength and an independent coupler that allows for the precise connection that such gears require as well as ready replacement of portions of the drive assembly without disturb-ing critical gear adjustment. Means are also used to provide fluid pressure support for the gyrating head to minimize wear, and furthermore fluid pressure lift is provided for portions of the drive connection to eliminate thrust loading of the outer radial bearing caused by the weight of the inner race of said bearing and parts mounted within the inner race. An ex-terior seal is provided which due to its particular construct-ion and disposition provides effective sealing during all con-ditions of operation of the crusher. Fluid drive means are associated with the bowl of the crusher for adjusting it ro-tatably by power and for locking the bowl in a fixed position.
The invention will be better understood and additional objects and advantages will become apparent from the following description taken in connection with the accompanying drawings which illustrate preferred forms of the device.
Figure 1 is an elevational view of the present crusher, certain parts of this view being broken away to show internal parts;
Figure 2 is a vertical sectional view showing internal working parts of the crusher;
Figure 3 is an enlarged detailed sectional view of an exterior seal structure;
Figure 4 is an~enlarged, fragmentary sectional view taken on the line 4-4 of Figure 2;
~ 3 ~ Z3~
Figure 5 is a horizontal sectional view taken on the line 5-5 of Figure 2, a portion of this view being broken away and also certain parts being omitted for clarity;
Figure 6 is a perspective view of a coupler utilized in a drive connection of the apparatus;
Figure 7 is a fragmentary sectional view taken on the line 7-7 of Figure 4;
Figure 8 is an enlarged, fragmentary sectional view taken on the line 8-8 of Figure 2;
Figure 9 is an enlarged~ fragmentary sectional view taken on the line 9-9 of Figure ~;
Figure 10 is a hori~ontal, fragmentary sectional view taken on the line 10-10 of Figure 2;
Figure 11 is a fragmentary plan view of a bearing support area for the head;
Figures 12 and 13 are enlarged, fragmentary sectional views taken on the lines 12-12 and 13-13 of Figure 11, respect-ively;
Figure 14 is an enlarged, fragmentary, foreshortened sectional view taken on the line 14-14 of Figure l;
Figure 15 is an enlarged detail view of a portion of Figure 14;
Figure 16 is a lragmentary elevational view tak~.l on the line 16-16 of Figure l;
Figure 17 is a fragmentary sectional view taken on the line 17-17 of Figure 16;
Figure 18 is a fragmentary elevational view showing a re].ief system operable upon the entry of non-crushable objects into the crusher;
Figure 19 is a fragmentary plan view taken on the line 19-19 of Figure 18;
~i L3~Z3~L
~ igurlc 211 i d f C.lg~llenl:ar'y pkln v:ie~ taken on the line '20-20 of Figure 14;
Figure 21 is a fragmentary elevational view taken on the line 21-21 of Figure 20;
Figure 22 is an enlarged, fragmentary sectional view -taken on -the line 22-22 of Figure 21;
Figure 23 is a view taken similar to Figure 14 but show-ing a modified structural arrangement for power ro-tation of the bowl;
Figure 2l~ is an enlarged, fragmen-tary sectional view taken on the line 24-24 of Figure 23i Figure 25 is a fragmentary eleva-tional view taken on the line 25-25 of Figure 23;
Figure 26 (on the sheet bearing Figure 20) is .1 fragmen-tary plan view taken on the line 26-26 of Figure 23;
Figure 27 (on the shee-t bearing Figures 2 and 3) is a fragmentary sec~ional view showing a modified bearing suppor-t for the crushing head; and Figure 28 (on the sheet bearing Figures 11, 12 and 13) is .' a view similar to Figure 2 but showing modified eccentric drive stnucture.
With par-ticular reference -to -the d:rawings and first to Figures 1 and 14, the crusher cor~lprises a lower circular body frame portion 25 reinforced by an upper integral annular ring 26 and a ~Lower in-tegral annular ring 27. The crusher is bolted or other-wise secured to ., suitable support 2~. Upright reinforcing webs 29 are welded to -the ex-terior of body por-tion 25 be-tween upper reinforcing rings 26 and 27. An oil reservoir 30 is formed a~ound the lower outer periphery of body portion 25 and flange 27 to 3~ provide good oil capaci-ty for lubrication of the crusher. This Mounting arrangement of reservoir 30 uses the body portion 25 as a hea-t sink.
The main body portiorl oE the crusher includes an inter-3~
nal centrally located ~ ~shaped frame portion 31, Figure 2,integrated with the circular frame portion by three or more I-beam type struts 32. The upper edge of frame portion 31 has a head support or thrust member 34 in the form of a ring re-movably attached thereto, and this head support has a spherical or dished upper bearing surface 35 which is engaged by a bottom arcuate surEace 36 on a crushing head 37 in a manner to be descri-bed more fully hereinafter. ~lead 37 supports mantle 38 on machined contact surfaces and by the medium of a filler layer 39 therebetween. A hold-down cap assembly 40 to be later described holds the mantle removably on the head.
With particular reference to Figures 1 and 1~, head 37 cooperates with an annular bowl 41 having a hollow frusto-conical surface 42 and having an inturned flange 43 below its upper edge which supports a liner 44 by means of eye-bolts 45 in a conventional manner. A hopper portion 46 is removably attached to the bowl 41 and directs rocks to be crushed into the area between the gyrating head 37 and the liner 44. Rock that has been crushed falls down around the exterior of ~rame 20- portion 31 and is carried away by suitable conveyor means not showm.
Input drive for the crusher comprises a shaft 50, Fig-ures 1 and 2, having an outward projecting end for securement to a drive sheave 51 rotated by suitable power apparatus not sho~m. The shaft 50 extends through an inwardly projecting housing 52 within a larger housing 52a. Sha~t 50 is supported by bearings 54 and housing 52 has an outside flange 53 abutted against the outer surface of housing 52a. This shaft and bear-ing assembly is installed and removed as a unit and housing 52 can be adjusted longi~udinally if necessary such as by shi~ing.
The inner end of shaft 50 has a bevel pinion gear 55 keyed or 3 ~ ~
otherwise secured thereto, and this pinion gear has meshing engagement with an annular bevel gear 56, also seen in Figure 4, removably secured to a flange 58 integral with a depending shaft 59 having journaled engagement in an annular upright housing 60 removably secured to the bottom of central frame portion 31. Journaled engagement of shaft 59 in the housing 60 is by upper and lower bearings 62.
Shaft 59 stabilizes flange 58 which drives an eccentric member 68 by means of an intermediate coupler 69, Figures 2 and 4-7. This coupler has a diametral groove 70 in its bottom sur-face and a diametral groove 71 in its top surface extending at right angles to the groove 70. A pair of spaced lugs or keys ~2 are releasably secured, as by screws 73, to the upper sur-face of flange 58 and slidably fit in the groove 70 of the coup-ler. Likewise, a pair of spaced lugs or keys 74 are releasably ; secured, as by screws 75, to the bottom surface of eccentric member 68 and slidably fit in grooves 71. Each of the lugs 72 and 74 fits in a recess 76 in the part to which it has screw connection.
The connection provided~by the coupler 69 thus comprises an independent connection between the drive gear 56 and the ; eccentric member 68. This independent connection, rather than comprising a direct connection between the gear and the eccen-tric member, accomplishes a first advantage of providing precise gear fit adjustment between the pinion gear 55 and the bevel gear 56. That is, such precise engagement can readily be accom-plis~ed if necessary by installing shims, not shown, between the flange of the bearing housing 52 and the housing 52a for horizontal adjustment and between the flange 58 and the gear 56 for vertical adjustment. Another advantage of the coupler 69 is that said coupler is of ~slightly less thickness than the spac- -~ 3~
ing between the flange 58 and eccentric member 68 and such clear-ance acco~nodates any misalignment and prevents vertical binding Furthermore, since the lugs 72 and 74 fit in recesses 76 in the parts to which they have screwed attachment, the rotating torque is taken directly by the coupler and the lugs and a shearing force is not put on the screws 73 and 75 The coupler 69 also has the advantage of simplifying accurate gear adjustment and replacement of associated parts in the field. Further yet, the coupler arrangement allows spiral bevel gears to be used, such type of gears having the advantage of being stronger and quieter than straight teeth gears.
A heavy shaft 80, Figure 2, is fitted into an axial bore 81 in the head 37 and has association, to be described, with the eccentric member 68 for producing the gyrating action of the head.
The hold-down cap assembly 40, which includes a torch ring 40a, has releasable engagement with the top end of the shaft for holding the mantle 38 in place. This cap is of conventional construction - -except for its threaded connection with the shaft 80. In this re-gard, the shaft has a threaded recess 82 arranged to receive a threaded bushing 83 also having internal threads for receiving a threaded shank 40b of cap 40. Since the outer threads on bushing 83 are stronger than the internal threads of said bushing because o~ their larger size, any failure of connection between the cap and the shaft will occur in the inner threads, thus eliminating damage to the shaft and usually only requiring a replacement of the bushing.
With particular reference ~o Figures 2, 8 and 10, eccen-tric member 68 has an integral upstanding housing 84 with the eccentric shape as best seen in Figure 10. This housing is jour-naled within a large self-aligning roller bearing assembly 85 seating at its bottom end on a shoulder 86 on frame 31 and on a shoulder 87 on the eccentric member 68. A sleeve 88 with an outer wall surface which is tapered inwardly toward the bottom is press t,~ .
fitted to the outer race of the bearing 85 and has wedging en-gagement in an upper portion 89 of the frame 31. Portion 8~
has a matching taper with the outer surface of sleeve $8. Thè
tapered sleeve 88 provides a means to press fit the outer race in place, such being necessary with the type of loading im-posed, and also this sleeve is easily removable which makes re-placement of the bearing 85 easy. A retaining ring 90 is re-leasably secured to a top flange of tapered sleeve 88 to pre-vent the bearing 85 from creeping upwardly. Retaining ring 90 may require shimming if the top face of sleeve 88 locates be-low the top face of the bearing 85. A lock nut 93 holds the eccentric member 68 from dropping out of bearing 85.
The bore housing 84 accommodates a cylindrical roller bearing assembly 95 whose inner race has a press fit on the shaft 80. A shoulder spacer 96 abuts against head 37 and has a slight clearance with a tapered portion 97 of the shaft 80. A
.retaining plate 98 bolts to the bottom of shaft 80 to properly position the inner race of bearing assembly 95 in place.
~ As best seen in Figure 2, the axis of shaft 80, de-signated by the nu~eral 99, is offset ~rom the axis 100 of the outer or-camming surface of the eccentric housing 84, and further-more-the inner bearing 95 and shaft 80 have tilted engagement within the inner bore of housing 94 by a selected angled bore of said housing whereby the axes 99 and 100 are offset at the bottom but meet at a vertex V at an upper portion of the crusher. ~pon rotation of the eccentric member 68, gyrating actions of the head 37, as designated by reference numeral 37a in Figure l, are accomplished.
The eccéntric member 68 has an extension 104 at one side-, Figures 2 and 5, which serves as a counterweight. In addi-tion, a counterweight 105, Figures 2 and 8, is releasably secured t~ the top edge of the housing 84 in an area approximately above the counterweight 104. Counterweight 105 also serves as ~~_ o ~ 3~3 ~
a retainer for the outer race of bearing 95. These counter-weights serve to balance the cen~rifugal force of the gyrating cone assembly so the entire crusher sits quietly on its founda-tion without imposin~ destructive shaking motions to said foundation.
As stated hereinbefore, the bearing surfaces for the head 37 in its gyratory crushing movements comprises the co-operating surface 35 on the head support 34 and surface 36 on the head 37. Such surfaces take massive thrust forces that can crush through hydrodynamic oil films and thus are subject to damage.
In order to provide maximum bearing life, however, and with re-~erence to Figures 2 and 11-13, surface 35 has an annular recess 108 which receives a plurality o~ arcuate segments 109 of bronze ; bearing ~laterial or a non-metallic low coefficient of friction material such as Teflon~Delrin~Nylatron~or other suitable material. Oil under pressure is admitted to the bearing surface between head 37 and inserts 109 through passageways 110 in the frame 34. A passageway leads-to each segment and`opens into-its bearing surface-, a combination duct and locating pin lll that is sealed against oil leakage at its outer diameter by O-rings. An enlarged recess 112 is formed-ln segments lO9 and has radiating grooves 113 for efficient distribution of the lubricating oil to the full surface OL the segments. The discharge of oil from the seg~ents 109 is through outlet passageways 114 in the head support 34 and in the segments 109, the passageways 114 communicating with end spaces 115 between the segments. The ends of segments 109 throughout a greater portion of their length ha~e an inward taper 116 for efficient pickup of oil to be discharged from the lubricated bearing surface.
The longitudinal edges of the segments lO9 have oil seals 117 of a suitable type ~Jhich will withstand high pressure and re-tain the lubricating oil between the two seals. The outer and inner edges of segments lO9 closely abut each other to reduce oil _ g_ ~3~
escaping under seals 117. A third seal 117a is disposed out-wardly from the outermost seal and is arranged to prevent inlet of dust and to wipe any escaped oil into an annular groov~
118 which is provided in the frame 34 and which com~unicates witn the drain 114. Drain 114 empties into the space above the bearings 85 and 95, Figure 2.
The inlet of oil through passageways 110 is introduced at high pressure and more particularly at a pressure which is greater per square inch than any possible working pressure on the head 37. Thus, a hydrostatic support is provided between the head 37 and the head support 34 to maintain a layer of lubri-cating oil between the surfaces and substantially eliminate any metal to metal contact under the most severe conditions, thereby keeping friction to the lowest possible value and mini-mizing wear. When attempting to re-start a crusher that has stalled due to overload, a-crusher without this hydrostatic fea-ture will 'h?ve this bearing surface in tight metal to metal contact, and- starting would have high-friction and bearing stresses. With this hydrostatic system, oil pressure will lift the cone head like a hydraulic jack. Metal bearing surfacesare separated before the crusher is started by suitable control means, and starting is easier and free of bearing damage. It is preferred that each segment have its own or individual pumping pressure to provide ; uniform and constant pressure support around the head, thus eli-minating migration of oil pressure to lower pressure working areas of the head. The oscillating surfaces between the two mem-bers spreads the lubricating oil in an efficient manner and in addition the head 34 tends to rotate slowly in a direction opposite to the rotation of the eccentric member 68. The resulting motion is a wave patiern on the bearing to provide a well lubricated, long wearing support of the head on the base frame.
.
23~
With ~efe~ence to ~igures 18 arld lg, a purr,p assembly is provided for the plurali-ty of se~ments 109 and cornprises individual pumps 119 secured on the crusher frame and disposed around a common gear case 120. Driving operation of the gear case is by motor 121 and connecting shaft 122. Individual pumps 119 are connected to respective segments 109 for reasons pointed out hereinbefore by individual conduits and passageways 123 and have intake from the oil reservoir 30 by sui-table condu:i-ts. One or more pumps 119 can be included in the pumping assembly for lubricating other bearings in Ln -thc assembly. An alternative to multiple pumps is one purnp followed by a series of flow dividers that are capable of maintaining even flow in two directions despi-te pressure differentials.
It is to be understood that although the use cf segmental inserts 109 are disclosed in the preferred embodiment, such inserts may be omitted and the hydrostatic pressure provided directly be-tween the metal surfaces of the head and *rame.
The combined weigh-ts of eccentric member 68, the inner bearing 95, the rollers, cage, and inner race of bearing 85, and , o-ther associated members attached to 68, are considerable and 20 would impose a significant -thrust load on the bearings 85 if not neutralized by some means. In this regard, and with reference par-ticularly -to Figure 4, a fluid pressure passageway 125 leads upwardly through the shaft 59 and has pr-essured supply through a conduit 126 fl~m suitable pump means such as a pump 119.
Passageway 125 eorrlnlurlicates with the interior of a cylinder 127 extending through a central opening 128 itl the coupler 69 and having a piston 129 therein. The upper end of this pis-ton has - an annular projection 130 which abu-ts against the lower surface of eccentric member 68. Pis-ton 129 has a preset relie* valve '(1 l3l therein, dnll t~lC ou-tlct ~rom this valve co~mul~icates with a port 132, also seerl in Figure 2, which leads -through eccentric member 68 wherel>y o:il passing through such port can flow acrosS
tllc upper suria(e ()l I lle eecQI~lri( Inc~ er 6B and ., . ,, . . . . .. , _ _ _ . .. . _ _ _ _ . . ... . .
,-- 113.-j231 ~
lubricate bearings 95. Piston 130 under the action of ~luid pressure will bear the weight of the eccentric member 68 and other parts, the relief valve 131 opening at pressures ~ -as near eq~lal as possible to the desired supporting pressure before admitting lubricating oil to the bearings 95 and other lubricated areas, to be described.
In adclition, a hollow piston 135 operates over a hub 136 formed in a bottom plate 137 releasably attached to the frame 31. The piston 135 is urged upwardly by a spring 138 into abutment with a hardened face bearing 139 having an O-ring seal therein. The area of hub 136 is greater than the face con-tac~ of piston 135 on the bearing 139 and thus oil pressure in passageway 125 which extends through all these members will hold the piston against the bearing and override the same oil pres-sure trying to separate them. The result is that piston 135 prodllces an upward lifting force on the shaft 59 sufficient to pre~ent excessive leakage from oil pressure in conduit 125.
; Suitable means, not sh'own, are associated'witX piston 135-'to prevent it from spinning on hub 136.
As stated, lubrication oil moving upwardly through port ; 132 will lubricate the inner bearing 95. The forced movement of such oil u?wardly will flow or be-thrown over into the area of the outer bearing 85, Figure 2, and also lubricate it. In addition, it is apparent that oil draining from the bearing surfaces 35 and 36 between the head and the frame will also provide some lubrication. Also, several passageways 142 lead downwardly from the area above the bearing 85 and empty into the interior of frame 31, and as shown one of such passageways empties into housing 52a above shaft housing 52. Oil draining through this latter passageway 142 is directed through a port 143 in the housing 52 by a baffle 144 for lubricating the bear-ings 54 Oil also drains down through bearing 85 into the bottom ~13S~3~
~of cup-shaped frame 31 and an oil level 145 is maintained for lubricating the gears. Housing 52a has co~-mnunication with the interior of frame 31 to serve as an additional reservoir, as well as to provide a cooling or heating area for the oil Because there is a creep fit between housing 84 and the inner race of bearing 85, it is desired that the engaging sur-faces between such inner race and the housing 84 be lubricated.
For this purpose and with reference to Figures 2, 8 and 9, a shield 148 is releasably secured to the upper edge of housing 84 and extends part way therearound. This shield is spaced a short distance above the top of the h~using 84 and is arranged to catch oil thereunder and direct it down through several passageways 149 co~unicating with an arcuate groove 150 in the outer surface of housing 84 and in the lock nut 93. By means of this groove, oil is distributed around for additional lubri-cation to bearing 85 so centrifugal force does not throw all the emerging oil beyond bearing 85. Lock nut 93 has several - passageways 151 leading outwardly from the groove 150 for direct-ing said oil to the bearing 85. Also, an auxiliary passageway 152 leads downwardly from passageway 149 and provides oil seepage between the inner race of bearing ~5 and the outer surface of housing 84.
-~ With reference to Figure 2, a frusto-conical seal 156 is secured between a ring 157 releasabl~ secured in a peripheral notch 158 in the bottom edge of a depending flange 159 of the head 37. T~e other end of the seal is connected to a ring 160 supported on a peripheral shoulder 161 in the head support 34.
Ring 160 is free to rotate relative to the support 34 and has bearing support in the groove 161 by bearing layers 162 of suita-` 30 ble bearing material such as non-metallic low coefficient of friction material. Seal 156 is formed of flexible and stretch-able material which is airtight and oil and ozone resistant.
o '.
~Z~l One acceptab]e material for this pllrpose is polyurethan2.
Importantly, this seal in its frusto-conical shape is directed substantially toward the vertex V whereby such seal will o?erate efficiently through all normal operating conditions of the head 37. That is, this seal due to its angular disposition will efficiently follow the gyratory movements of the head with the least amount of stretching and at the same time can rotate ~ith the head by movement of the ring 160 on the shoulder 161 and bearing 162. This seal will protect the internal workings of the crusher from the entrance oE dust, although in the remote circll;nstances that such seal should fail, the outer seal 117a of bearing surfaces 35 and 36, best seen in ~igure 12, will keep dust from entering the bearing surfaces and interior of the machine. The upper end of ring 160 is tapered downwardly at 163 toward the center to drain oil which may have escaped into such area back into the drain 114. An inclined port 164 leads from such iapered surface 163 to the drain 114.
With reference to Figure 3, the ring 157-has a passage-way 165 therethrough for draining oil through the seal wnich may have escaped into the lower area of the seal, such oil merely dripping out to the exterior of the apparatus. A ~ilter 166 is mounted in the ring 157 across the pa-ssageway 165 to prevent the entrance of dust upwardly through the passageway.
A bowl support 170, Figures 1 and 14 (also seen in a modification view of Figure 23) has an upper peaked portion 171 and a lower notched portion 172 arranged to seat on the annular reinforcing ring 26 and to extend down in a pressed fi~ into the top portion of body frame portion 25. Bearing liners 173 of suitable material such as l~icarta~are bonded to the ring 26 and machined portion of frame 25. Bowl support 17~ can slip relative to the base if a sufficient and generally abnormal torque is present and such comprises an important advantage of the instant apparatus because it relieves undersirable torque in the frame.
~3;323~
It is desired t'nat the bowl support 170, although being able to slip relative to the frame, be held against vertical movement off the frame, and for this purpose several clamps 175, Figure 16 (and also Figure 23) are bolted to the ring 26 and have finger projection into a peripheral groove 176 in the support 170.
Seated on the bowl support 170 is an annular frame or large nut 179 having an outwardly projecting flange 180 and also having an inYerted V-shaped groove 181 in its bottom sur- -ace for seating engagement on the support 170. Nut 179 has internal threads 182 having meshing engagement with exter-nal threads 183 on the bowl 41.
During hard crushing, there is a tendency for the bowls of cone crushers to lift slightly or float on the frame support. This action creates enormous torques that want to drive the bowl circularly relative to the supports. In order to prevent such rotation, several depending stops 186 on the nut 179, Figures 1 and 16, abut against upstanding companion stops 187 on the--ring 26. Rotation is thus prevented between the nut 179 and the base frame in the one direction, but as stated, the bowl support 170 can slip if forces are great enough, The engaging faces of the stops 186, 187 are angled slightly to allow tneir top edges to miss each other when closing back together from a separation. These stops may be made to face in opposite directions than that shown for reverse rotation of the input shaft, or if desired stops that work both ways can be used.
The floating movement of the nut 179 on the bowl support 170 is controlled by a fluid operated hold-down mechanism compri-sing a plurality of fluid operated cylinders 190, Figures 16-l9, spaced around the exterior of the crusher frame and associated with a tram? iron relief system. The upper end of each cylinder 190 is bolted to the ring 26, such c-~linders have pis~ons l91 engage-a ~35'~
able with thrust rods 192 extending in sealed engagement through the lo~Jer end of the cylinders into abutment at their lower ends against beams 193. The ends of the rods 192 are rounded and engage rounded portions of the pistons 191 and beams 193 for pivotal adjustment. Each beam 193 pivotally supports a pair of eye nuts 194 at opposite ends thereof and these eye nuts have vertical grooved guided engagement with vertical guides 195 secured to the webs 29. A pair of vertical rods 196 have threaded engagement at their lower ends with respective eye nuts 194, and these rods pass freely through ring 26 and the flange 180 of nut 179. The upper end of rods 196 receive hold-down nuts 197 and spring washers 198 between the nuts and the flange 180. Thrust rods 192 are held tightly in place between their pistons 191 and beams 193 by the spring washers 198 and by the tramp iron relief system now to be descri-bed.
Manifold sections 200 are coImected to upper portions of two or more of adjacent ones of relief cylinders 190 to-provide co~munication of these sets of cylinders with each other. One of the manifolds communicates with a pressure switch 201 by a conduit 202. Switch ~Ol has electrical connection by wires 203 with an electric motor 204. Switch 201 controls operation of motor 204 and will start the motor upon a selected lowering of pressure in manifold 200, as will be more apparent hereinafter.
Motor 20~ drives a hydraulic pump 205 connected on its input side to a pair of accumulators 206 by a conduit 207. Accumu-lators 206 are in communication with each other by a manifold 208. A third manifold 209 extends around the machine adjacent to manifold 208 and has communication with all the manifolds 200 by vertical connecting conduits 210.
A valve assembly 212 is connected to manifolds 208 and 209 and has a valve chamber 213 associated with manifold 208 1~3~23~
and a valve cha~ber 214 associ~ted wi~h manifold ~09. A sprin~
loaded plun~er valve 215 operates between valve chambers 213 and 214 and is arranged to control ~luid flow ~rom charnber 214 to chamber 213 in one direction, the latter chamber being en-larged at 213a around the plunger to allow free passage of fluid between the two accumulators 206. Valve 215 is selectively pre-loaded by a spring assembly 216, preferably comprising a stack of spring washers, thrusting agai~t an auxiliary plunger 217 having a ball and socket engagement 218 with plunger 215. Ball and socket connection 218 preve~ts any binding of plunger 215.
A pair of ball check valves 220 as well as valve 215 stops fluid flow under normal conditions from chamber 214 to cnamber 213, the check valves 220 being held in operative position ; by retaining pins 221. A conduit 222 leads from the outlet of pump 205 to chamber 214 of valve assembly 212, this conduit ;
having a check valve 223 therein to prevent oil from bleeding back into the pump. Chamber 214 has a manually operable relief valve 224 to drain the pressure from the system.
The relief system is set up ~or operation as follows;
The cylinders 190 and-their-manifolds 200 and 209-, as well as chamber 214 in valve assembly 212, are pressurized at a specific prPssure, Ior example, 2500 PSI, this pressure comprising a de-sired-hold-down--force for illustration purpose. The lower chamber 213 of valve assembly 212 as well as the accumulators and-manifold~208 are pressurized at a pressure a ~ew hundred pounds lower than the pressure in chamber 214 and its associated parts, ~or example, 2100 PSI. The accumulators 206 are initially charged to approximately 1800 PSI with nitrogen gas. Oil is then pumped into the accumulator system to raise the pressure to the desired 2100 PSI. This builds up an ample reservoir of oil for pump 205 to keep chamber 214 suitably charged as will be descri-bed. The pressure in the accumulators will vary according to temperature but the pressure in chamber 214 will be substantially o 3~3~
.constant. Spring 216 is pre-loaded to allow plunger valve 21~
to open at a higher pressure than that which exists in chamber 21~, for example, 2750 PSI. The pressure switch 201 is arranged to energize the pump motor 204 when the pressure drops a slight amount below the pressure in the relief cylinders, for example, 2475 PSI. In normal operation, some slight up and down move-ment of the bowl 41 and nut 179 will exist. This slight move-ment will be absorbed by the springs 198. Such spring action prevents damaging fluttering movement of the pistons 191 in their cylinders 190.
~owever, when a non-crushable object such as a piece of "tramp iron" enters the crusher, the bowl 41 and nut 179 raise more than normal as the cone-shaped head 37 presses against the obje~t. The pistons 191 in the relief cylinders 190 in that particlllar section of the relief system rise and hydraulic fluid flows ;:hrough manifolds 200 and 209 into valve chamber 214 and push the plun~er 215 open. Fluid then flows into chamber 213 of valve assembly--212 to-provide relief ln-the cylinders-l90- -and thus in the hold-down function. The accumulators 206 absorb fluid entering valve chamber 213 and manifold 208. As the cone gyrates away Lrom the object, the fluid returns from chamber 213 to chamber 214 through ball check valves 220. This action repeats until the object has cleared the crusher and as is appar-ent the pressure in the two valve chambers 213 and 214 wi.ll be substantially the same. As soon as the pressure in manifold 200 gets below a selected value, namely 2475 PSI in this illustration, switch 201 starts motor 204 for restoring normal pressure to valve chamber 214 and of course the relief cylinders 190. In this arrangement, the pump only has to raise the pressure a small amount, for example, from the lowered pressure to the 2500 PSI
normal. Such eliminates the necessity of the pump having to raise the pressure back up from zero.
3 ~ ~3~
It is necessary to firmly jam or lock the thread engagement between bowl 41 and t.he nut 179 to maintain desired crusher adjustment and to resist destructive movement during crushing operations and when violent inertial action occurs from non-crushable objects passing through the crusher. For this purpose, an annular jam nut 230, Figure 14, seats on the top edge of nut 179 and threadedly engages the threads 1~3 of the bowl. A non-metallic low coeff:icient of friction bearing washer 231, also seen in Figure 15, is disposed between the jam nut 230 and the nut 179. With particular reference to Figure 15, thread liners 232 which may also be constructed of a non- i metallic low coefficient of friction bearing material are secured between the threads 182 and 183. Preferably, these liners are secured to the threads 182 on the nut 179. The threads and liners are dimensioned and arranged such that those :~ on the bottom surfaces of threads 182 fill the space between the - threads 182 and 183. These threads take the upward thrust of - bowl 41 during crushing operatlons. The liners on the upwardly facing surface of threads 182 have clearance with threads 183 and merely serve as bearing surfaces when the crusher is being adjusted. A liner 233 may also be provided be~ween an upwardly facing surface of one or more threads of jam nut 230 and threads 183. The liners 232 and 233 reduce the unlocki.ng force required to release nuts 179 and 230 and provide assist in the adjus~ent of che crusher while crushing by eliminating metal to metal con-tact and a much reduced coeffici2nt of friction. These liners also prevent seizing of the threads by galling or corrosion.
An upright sleeve 235 is secured, as by welding, to the outer peripheral surface of jam nut 230 with portions there-of projecting above and below the jam nut. Attached to theinner surface of the lower projecting portion of sleeve 235 are one or more depending arms 236) Figures l and 16, pivotally o 3~
.connected to one end of a ~luid operated cylinder 237. The ' other end of cylinder 237 is pivotally anchored to a post 238 integrated with the ~lange 180 of nut 179. The working move-ment of the fluid o?erated cylinders 237 is such as to ~ully release the jam nut 230 in one direction of movement and to fully lock the jam nut in the other direction of movement. Two of the cylinder assemblies 237 are disposed in diametrical re-lation on the machine and are used to balance the torque drive.
The fluid operated cylinders 237 are selectively disposed and the thread arrange~ent is such that the cylinders utilize a pus~ing movement of their pistons to unlock the jam nut 230, thus utilizing the greater power of the pistons as compared to their pulling ?ower to release the break-out torque and friction re~ d which is greater than the locking friction. Because it i: r,landatory to unlock the system before adjustment can be made, ~e cylinders must have enough thrust to accomplish this ; unlo.~lng and rotating function. Means are provided for the power rotaijS~n of bowl 41 for functions of its installation, removal, or adjustment, and for tnis purpose, an annular angular housing 242, Figures 1 and 14, is bolted to the top edge of the bowl 41 and made dust tight therewith by an-O-ring seal 241. Housin~
242 extends downwardly in partial overlapping relation with the sleeve 235, and a combination bearing and dust seal 243 is dis-posed between the overlapping portions to allow a sealed bear-ing rotation between these parts. The exterior of the housing has a plurality of evenly spaced vertical projections or lugs 244.
One or more truss-like members 246, Figures 14 and 20-22, have an inte~ral bottom plate 247 bolted to brackets 248 welded to the nut 179. Two fluid operated cylinders 249 are pivotally anchored to end posts 250 and are pivotally connect-ed at their other ends to respective lever arms 252 integral with upright sleeves 253 pivotal on shafts 254 supported in the truss - member 246. The upper ends of sleeves 253 have a lever arm 256 -20.
which is pivotally connected to one end o a pawl 257 having a hook end 258 arrar.ged for pulling engagement with projections 244. Pawls 257 are urged rotatably toward the housing 242 into engage~ent with projections 244 by means of torsion springs 259 contained on a depending extension 260 of the pivot supp~rt for the pawl.
The ends of the pawls 257 opposite from the hook end have an integral extension 263 projecting under the lever arm 256 and terminating in a second hook 264. These hooks are associated with stops 265 on the undersurface of arms 256. The arrangement is such that upon retracted movement of the fluid operated cylinders 249 to a point where the arms 256 and pawls form approximately a straight line, the hooks 264 engage stops 265 to stop the action of the springs 25~ on their pawls 257, whereby continued retracting movement of the cylinders causes the pawls to swing clear of lugs 2k4.
In the operation of the power rotating means for the bowl 41, one cylinder 249 will drive while the other one re-tracts whereby upon repeated operations, the bowl can be ratcheted in the direction desired. The controls for operating the cylinders 249 are not shown but their operation is readily accomplished by conventional valving either under manual control or by auto-matic control. Rotation of the bowl for adjustment vertically or for releasing it after crusher use will take place of course only after release of the jam nut 202 which will again be tight-ened when rotation of the bowl has been completed.
A modified form of power rotative adjust~ent of the bowl is shown in Figures 23-26. Tnis embodiment also shows a slightly different bowl and jam nut construction wherein the jam nut 230' has a sleeve 235' bolted to the upper surface thereof which projects upwardly in close association to the threads-183 of the bowl. An angular housing 242' on the bowl overlaps a portion of the sleeve 235'; a combination seal and bearing t~ -21-~ 3~
243' being provided betwf en the overlapping portions. Evenly ' spaced projections or lugs 244' are provided on the bowl.
A vertical plate 268 is bolted to brackets 269 welded to the nut 179, and such plate supports integral posts 270 at opposite ends thereof. One of the ends of a pair of fluid operated cylinders 271 is connected to the respective posts and the ends of the piston rods are pivotally connected to notched ends 272 OI a single pawl or slide block 274. Pawl 274 has a centrally located inner edge notch 275 and a pair of shallow end notches 276. As will be more apparent hereinafter, the pawl 274 is arranged to drive the bowl in either direction, and as best seen in Figure 24 the notches 275 and 276 are arranged such that the pawl will engage two of the projections 244' at a time for driving in either direction. A cap screw ; 277 passes through an elongated guide slot 278 in a curved ; guide plate 280 and is threadedly engaged with the pawl 274.
Cap screw 277 is adjusted with sufficient clearance so as to have slidable guided movement of pawl 274 against plate 280.
A cap plate 281 is bolted to the top of pawl-274 and overlaps the plate 280 to shield the slide surface from dust and assist in the stabilization of pawl 274.
A pair of spaced standards 283 are secured integrally to the nut 179 and pivotally support at their upper ends a lever arm assembly 284 having an upright body portion 285 secured integrally to the bottom of the pawl supporting plate 280. A toggle assembly 286 is pivotally supported at the lower ends of the standards 283> and such toggle assembly is pivotally connected to the upper lever arm assembly 284 by-two toggle links 287. An upright fluid operated cylinder 289 is pivotally support-ed at its lower end on a bifurcated arm 288 integral with toggleassembly 286. The upper end o~ cylinder 289 is pivotally connected to lever arm assembly 284. As seen in ~ull and broken lines in Figure 23 such cyli~der is arranged to pivot the upper 1~35~3~L
lever arrn assembly and the toggle assembly to e~tend or closethe pawl 274. Tne toggle links have stops 292 which limit overcenter movement in an outward direction.
The two fluid operated cylinders 271 operate in unison, namely, they assist each other in both directions of operation.
When it is desired to turn the bowl of the crusher, fluid operated cylinder 289 is first extended to place the pawl 274 in engage- --ment with projections 244'. Jam nut 230' is then unlocked, the cylinders 271 are driven in the desired direction and upon com-pletion of their travel, the cylinder 289 is retracted to release the pawl 274. The cylinders 271 are then operated in the opposite direction to move to a new drive position at which time the cylinder 289 again moves the pawl inwardly. This procedure is repeated to provide the desired rotation. When the desired ro-tation is made and a crllshing operation is to take place, the jam nut 230' is tightened by means of its fluid operated cylinder.
The pawl construction of the embodiment of Figure 23 has the advantage that the bowl cannot overrun when adjusting since the pawl will catch and hold any such over-running rotation. Also, since the two fluid operated cylinders work together, half as large a cylinder area is required as compared to whereone fluid operated cylinder does the work. Either adjusting system of Figure 20 or Figure 26 will work with either housing 242 or 242', Referring to Figure 27, a modified bearing support bet~een the cone-shaped head 37' and the head sup?ort 34' is illustrated. In this embodiment, a bearing insert 294 is set in a recess 295 in the head 37' and has a spherical botto~ surface engaging the dished supporting surface of head support 34`.
Insert 294 may be replaced as necessary.
P~eferring to Figure 28, a modified form of eccentric drive ls shown for the main upper shaft 80'. In this modifica-tion, the eccentric member is a triple race bearing having an eccentric middle race ~4a' and-is similarly driven from below 3;~Z3~
as in the fi~st embodi~lent. It also employs a counterwei~ht portion 104'. The middle race ~4a' has a driving flange 68' bolted to its lower face and carries a counterweight 105' at its upper face. Middle race 84a' is journaled bet~7een an inner set ff of rollers and an outer set of rollers. Its outer surface thus coMprises the inn~r race for a large self-aligning roller bearing 85' engageable with an outer race 84b'. Outer race ~4b' seats on the shoulder 86 of the frame 31. The middle race 84a' forms the outer race of roller bearings 95' whose inner race 95a' 10 has a press fit on the shaft 80'. A shoulder spacer 96' and a retaining plate 98' hold the inner race 95' in place. As in the first embodiment, a tapered sleeve 88' is press fitted within the frame 31, and a retaining plate-90' is bolted to the top of this sleeve to hold the outer race 84b' in place.
The eccentric and drive arrangement of the embodiment of Figure 28 is similar to that illustrated in Figure 2 with the exception that the eccentric midrace 84a' is utilized also as bearing races on opposite surfaces thereof, thus minimizing the number of parts necessary in this radial bearing area and provi- ¦
20 ding a more-compact design.
According to the present invention, a gyrating or cone-type crusher is provided which is extremely efficient in operation and which is relatively simplified and inexpensive to manufacture. The parts operate efficiently with a minimum of wear and are arranged for easy replacement. In addition, the inner parts are effectively sealed against the inlet of dust or foreign particles to further prolong the working life of the parts.
Further yet, means are provided to minimize damaging strains in the various parts and also, power adjustment of the bowl facilitates 30 operation of the crusher by a single person.
It is to be understood that the form of my invention herein shown and described are to be taken as preferred examples ~ -24-~13~31 " ~ ~.
of the same and that various changes in the shape, size and arran~ement of parts may be resorted to without departir,g from the spirit of my invention, or the scope of the subjoined claims.
~ - .
,
Claims
The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:
1.
A rock crusher comprising (a) a base frame, (b) a crusher head on said base frame, (c) a mantle seated on said head, (d) a bowl on said frame associated with said mantle to form a crushing area, (e) shaft means having a top surface, (f) eccentric means operable with said shaft to produce gyratory movement upon rotation of said eccentric means, (g) a threaded recess in the top surface of said shaft means, (h) a threaded hushing removably engageable in said threaded recess and having inner threads, (i) a cap member arranged to bear down on said mantle to hold the latter down on said head, (j) and an integral depending shank on said cap arranged for removable engagement with said inner threads to removably hold said cap down on said mantle.
2.
A rock crusher as claimed in claim 1, wherein the internal threads of said bushing are less mechanically strong than the external threads thereof.
1.
A rock crusher comprising (a) a base frame, (b) a crusher head on said base frame, (c) a mantle seated on said head, (d) a bowl on said frame associated with said mantle to form a crushing area, (e) shaft means having a top surface, (f) eccentric means operable with said shaft to produce gyratory movement upon rotation of said eccentric means, (g) a threaded recess in the top surface of said shaft means, (h) a threaded hushing removably engageable in said threaded recess and having inner threads, (i) a cap member arranged to bear down on said mantle to hold the latter down on said head, (j) and an integral depending shank on said cap arranged for removable engagement with said inner threads to removably hold said cap down on said mantle.
2.
A rock crusher as claimed in claim 1, wherein the internal threads of said bushing are less mechanically strong than the external threads thereof.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000381740A CA1135231A (en) | 1978-04-17 | 1981-07-14 | Mantle |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/897,289 US4192472A (en) | 1978-04-17 | 1978-04-17 | Cone crusher |
| US897,289 | 1978-04-17 | ||
| CA311,363A CA1122946A (en) | 1978-04-17 | 1978-09-15 | Cone crusher |
| CA000381740A CA1135231A (en) | 1978-04-17 | 1981-07-14 | Mantle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1135231A true CA1135231A (en) | 1982-11-09 |
Family
ID=27165855
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000381740A Expired CA1135231A (en) | 1978-04-17 | 1981-07-14 | Mantle |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1135231A (en) |
-
1981
- 1981-07-14 CA CA000381740A patent/CA1135231A/en not_active Expired
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| MKEX | Expiry |