CA1235679A - Cone crusher - Google Patents
Cone crusherInfo
- Publication number
- CA1235679A CA1235679A CA000433110A CA433110A CA1235679A CA 1235679 A CA1235679 A CA 1235679A CA 000433110 A CA000433110 A CA 000433110A CA 433110 A CA433110 A CA 433110A CA 1235679 A CA1235679 A CA 1235679A
- Authority
- CA
- Canada
- Prior art keywords
- eccentric
- oil
- bearing
- skirt
- cone crusher
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000005461 lubrication Methods 0.000 claims abstract description 35
- 230000033001 locomotion Effects 0.000 claims abstract description 24
- 239000003921 oil Substances 0.000 claims description 123
- 239000000463 material Substances 0.000 claims description 13
- 239000010687 lubricating oil Substances 0.000 claims description 12
- 229910000897 Babbitt (metal) Inorganic materials 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 4
- 230000005484 gravity Effects 0.000 abstract description 5
- 239000000314 lubricant Substances 0.000 abstract description 5
- 230000000694 effects Effects 0.000 abstract description 3
- 230000013707 sensory perception of sound Effects 0.000 abstract 3
- 230000009471 action Effects 0.000 description 7
- 210000001364 upper extremity Anatomy 0.000 description 7
- 210000003141 lower extremity Anatomy 0.000 description 6
- 239000000428 dust Substances 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000012856 packing Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 210000003414 extremity Anatomy 0.000 description 2
- 210000002414 leg Anatomy 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000011435 rock Substances 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 239000010425 asbestos Substances 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 238000011065 in-situ storage Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 210000001699 lower leg Anatomy 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012806 monitoring device Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000000063 preceeding effect Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 229910052895 riebeckite Inorganic materials 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000010913 used oil Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C2/00—Crushing or disintegrating by gyratory or cone crushers
- B02C2/02—Crushing or disintegrating by gyratory or cone crushers eccentrically moved
- B02C2/04—Crushing or disintegrating by gyratory or cone crushers eccentrically moved with vertical axis
- B02C2/047—Crushing or disintegrating by gyratory or cone crushers eccentrically moved with vertical axis and with head adjusting or controlling mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
- F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
- F16C23/048—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for axial load mainly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/1045—Details of supply of the liquid to the bearing
- F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Food Science & Technology (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Crushing And Grinding (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
Cone crushers of the gyratory type, which incorporate an eccentric, rotatable about a stationary shaft, and which coacts with the depending skirt, of the movable crushing tool support cone, to impart a gyratory motion to the movable crushing tool. The invention contem-plates: providing a combination of both plain and roller hearings to mount the eccentric in the crusher, and for coaction with the lower crushing tool mounting cone; pro-viding the main thrust bearing assembly, which also serves to support the lower crusher tool mounting cone, with coacting surfaces that facilitate proper and complete lubrication of the hearing; providing a direct and efficient path of lubricant flow to the main thrust bearing assembly for all positions of adjustment of the crusher gap; pro-viding lubrication channels and flow patterns that insure proper lubrication of the plain hearing, and for that matter lubrication to all bearings that reach the bearing after being filtered and cooled and without first passing through other bearings; providing a counterweighted flywheel that is fabricated to not only offset the rotational effect of the eccentric but also with its rotational forces located and distributed to minimize unwanted moments about the center of gravity of the crusher.
Cone crushers of the gyratory type, which incorporate an eccentric, rotatable about a stationary shaft, and which coacts with the depending skirt, of the movable crushing tool support cone, to impart a gyratory motion to the movable crushing tool. The invention contem-plates: providing a combination of both plain and roller hearings to mount the eccentric in the crusher, and for coaction with the lower crushing tool mounting cone; pro-viding the main thrust bearing assembly, which also serves to support the lower crusher tool mounting cone, with coacting surfaces that facilitate proper and complete lubrication of the hearing; providing a direct and efficient path of lubricant flow to the main thrust bearing assembly for all positions of adjustment of the crusher gap; pro-viding lubrication channels and flow patterns that insure proper lubrication of the plain hearing, and for that matter lubrication to all bearings that reach the bearing after being filtered and cooled and without first passing through other bearings; providing a counterweighted flywheel that is fabricated to not only offset the rotational effect of the eccentric but also with its rotational forces located and distributed to minimize unwanted moments about the center of gravity of the crusher.
Description
~Z35!679 CONE CKUS~ER
-BACKGROUND OF T~ VENTIO~
This invention relates to cone crushers; and more parti cularly to cone crushers of the gyratory type.
S BACKGROUND OF THE I~VENTION-DESCRIPTION OF THE PRIOR ART
. . _ . _ _ _ _ _ . . _ _ _ _ _ .
The crushing action, of cone type crushers, results from the gyratory movement o~ a movable crushing tool with ras~
pect to a stationary crushing tool, and the coaction between both said tools upon the materLal to be crushedO A driven eccentric coacts with the movable crushing tool, through co-operating bearing surfaces~ to impar~ the gyratory movement to the movable crushing tool; and to permit the relative rotary movement between the movable crushing tool and -the eccentric required during the crushing operation.
Crus`hers such as those shown in U~S. Patents 3,227,381 and 3,417,932 which utilize only plain bearings between the bearing sur~aces, may unnecessarily waste energy to overcome the friction ~orces inherent in plain bearings. On the other hand, crushers, such as shown in U~S~ Patents ~O 3,396,916 and 3,759~453 which utilize only roller bearings between the bearing surfacesO require relatively complex ~ .
~356~9 arrangementS for effec-ting adjustment o-E the spaciny of the crushing tools, and for relief of thc~t spacing when uncrush-able material, such as tramp iron~ ~alls into the crushing chamber. When these crusher spacing adjustment arrangements are applied to the upper crushing tool they quite often dictate the use of heavy coil springs, or hydraulic cylin-ders, externally disposed about the periphery of the upper portion of the crusher. The adjustment action of the springs or hydraulic pistons have been known to injure operators and result in requirements for expensive and cumbersome guards.
If the crusher spacing adjustment is -to be applied to the type of cone crusher with a vertically adjustable lower crushing tool, then the required relative linear movement between bearing faces results in highly complex and expensive bearing mechanisms.
Thorough and continuous lubrication of the multitude of bearings and bearing surfaces in the cone crusher is required if the crusher is to function effectively and efficiently. However, existing systems for supplying lubri-~0 cating oil to the crusher bearings; such as those shown in U.S. Patents 3,~1~,932 and 3,692~249, have been found lacking because the lubricating oil is routed through one bearing after another before it is cooled and filtered; and lZ3~679 because existing systems quite often merely utilize existing spaces as oil paSgageS thus accep-ting the too much, or just enough oil, that flows to or through a particular bearing rather than providing ~le proper amount o~ lubricant for the bearing service.
A main, or spherical bearing assembly is utilized in many cone crushers for mounting -the movable crushing tool support member or mounting cone so as to facilitate the gyratory movement of the movabl~ crush;ng -toolO Here again, proper lubrication of the bearing surface is important and not always accomplished in existing cone crushersO
An essential component 'in cone crushers of the gyratory type is a flywheel counterweighted so as to counterbalanc~
the effect of the rotating eccentric. In cone crushers of the type shown in U.S. Patent 2,359,987 and 2,814,450 the counterweight is formed by pouring lead into a pocket provided in available space in the casting that also includes the drive gear for the eccentric. This sometimes results in a counterweight whichJ while counterbalancing the .0 e~fec-ts o~ the eccentric 9 may create other undasirable forces. In additionJ -there appears to be inherent inaccura-cies and complexities in so forming the counterweights.
12;~56~79 Similarly counterweights formed and located as shown in U.S. Patent 1,945,791 have also proved less than ideal for the required purpose. More ls required than merely sticking a weight of proper size in an available space.
`SUMMARY OF T~E INVENTION
Broadly speaking, the present invention provides a cone crusher comprising: frame means; center shaft housing means carried by the frame means; bore means formed in a central portion of the center sh~ft housing means;
center shaft means, disposed in the bore means of the center shaft housing means, movable in an axial direction with respect to the center shaft housing means but rotationally stationary with respect to the center shaft housing means; piston means coacting with the center shaft means for moving the center shaft means in the axial direction; eccentric means rotatably disposed about the center shaft housing means; drlve means connected to the eccentric means to drive same in a predetermined driven direction; crusher head means carried by the center shaft housing means and having skirt means disposed for coaction with the eccentric means such that when the eccentric means is driven by the drive means the crusher head means is gyrated and rotated with respect ~o the eccentric means;
plain bearing means disposed between coacting surfaces of LCM:mls :1~35~
the eccentric means and the skirt means; and roller bearing means disposed between coacting sur~aces of the eccentric means and the center shaft housing means.
Thust this invention involves new and improved cone crushers, of the gyratory type, which incorporate an eccentric, rotatable about a stationary shaft, and which coacts with the depending skirt, of the movable crushing tool support cone, to impart a gyratory motion to the movable crushing tool. The invention contemplates:
providing a combination o~ both plain ~nd roller bearings to mount the eccentric in the cr~usher, and for coaction with the lower crushing tool mounting cone; providing the main thrust bearing assembly, which also serves to support the lower crusher tool mounting cone, with coacting surfaces that facilitate proper and complete lubrication of the bearing; providing a direct .
. ~
~ LCM:mls ~Z356~9 and efficient path o~ lubricant flow to the main thrust bea~ing assembIy for all positions of adjustme~t of the crusher gap; providing lubrication channels and flow patterns that insure proper lubrication of the plain bear-ing, and for that matter lubrication to all bearings that reach the bearing after being ~iltered and cooled and without first passing through other bearings; providing a counterweighted flywheel that is fabricated ko not only offset ~he rotational effect of the eccentric but also with its rotational forces located and distributed to minimize unwanted moments about the center of gravit~ o~ the crusher.
Other ob~ects, features, and advantages of the invention in its details oE construction and arrangement of parts will 1~ be seen from the above; from the following description of the preferred embodiment when considered with the drawing and from the appended claimsO
BRIEF_DESCRIPTION OF-THE DRAWING
In the drawing:
~0 FIG. 1 is a vertical ~levation of a ~piderless gyratory cone crusher, incorporating the instant invention, secti.oned in part and with ~ome parts shown out of rotation to better show details thereof, lZ35679 FIG. 2 is an enlarged view of a portion o the sectioned showing of the crusher of E~IG. 1, FIG. 3 is a further enlargement of a portion of FIG. 2 showing details of some lubrication flow paths, and of other S components o the crusher;
FIG. 4 is a sectional view taken on line 4-4 o FIG. l;
FIG. 5 is a plan view of the ball sector of the main thrust bearing assembly for the cone crusher of FIG. l; and FIG. 6 is a partial sectional view, o the flywheel sub-assembly for the cone crusher, showing the counterweight pouring mold in place during the counterweight forming , process.
I
BRIEF DESCRIPTI0~-OF-THE PREFERRED EMBODIMENT
For convenience, the invention will be described as applied to a spiderless gyratory cone crusher; it being understood, nevertheless, that without departing from the scope of this invention; that the combination plain bearing/roller bearing mounting or the eccentric and
-BACKGROUND OF T~ VENTIO~
This invention relates to cone crushers; and more parti cularly to cone crushers of the gyratory type.
S BACKGROUND OF THE I~VENTION-DESCRIPTION OF THE PRIOR ART
. . _ . _ _ _ _ _ . . _ _ _ _ _ .
The crushing action, of cone type crushers, results from the gyratory movement o~ a movable crushing tool with ras~
pect to a stationary crushing tool, and the coaction between both said tools upon the materLal to be crushedO A driven eccentric coacts with the movable crushing tool, through co-operating bearing surfaces~ to impar~ the gyratory movement to the movable crushing tool; and to permit the relative rotary movement between the movable crushing tool and -the eccentric required during the crushing operation.
Crus`hers such as those shown in U~S. Patents 3,227,381 and 3,417,932 which utilize only plain bearings between the bearing sur~aces, may unnecessarily waste energy to overcome the friction ~orces inherent in plain bearings. On the other hand, crushers, such as shown in U~S~ Patents ~O 3,396,916 and 3,759~453 which utilize only roller bearings between the bearing surfacesO require relatively complex ~ .
~356~9 arrangementS for effec-ting adjustment o-E the spaciny of the crushing tools, and for relief of thc~t spacing when uncrush-able material, such as tramp iron~ ~alls into the crushing chamber. When these crusher spacing adjustment arrangements are applied to the upper crushing tool they quite often dictate the use of heavy coil springs, or hydraulic cylin-ders, externally disposed about the periphery of the upper portion of the crusher. The adjustment action of the springs or hydraulic pistons have been known to injure operators and result in requirements for expensive and cumbersome guards.
If the crusher spacing adjustment is -to be applied to the type of cone crusher with a vertically adjustable lower crushing tool, then the required relative linear movement between bearing faces results in highly complex and expensive bearing mechanisms.
Thorough and continuous lubrication of the multitude of bearings and bearing surfaces in the cone crusher is required if the crusher is to function effectively and efficiently. However, existing systems for supplying lubri-~0 cating oil to the crusher bearings; such as those shown in U.S. Patents 3,~1~,932 and 3,692~249, have been found lacking because the lubricating oil is routed through one bearing after another before it is cooled and filtered; and lZ3~679 because existing systems quite often merely utilize existing spaces as oil paSgageS thus accep-ting the too much, or just enough oil, that flows to or through a particular bearing rather than providing ~le proper amount o~ lubricant for the bearing service.
A main, or spherical bearing assembly is utilized in many cone crushers for mounting -the movable crushing tool support member or mounting cone so as to facilitate the gyratory movement of the movabl~ crush;ng -toolO Here again, proper lubrication of the bearing surface is important and not always accomplished in existing cone crushersO
An essential component 'in cone crushers of the gyratory type is a flywheel counterweighted so as to counterbalanc~
the effect of the rotating eccentric. In cone crushers of the type shown in U.S. Patent 2,359,987 and 2,814,450 the counterweight is formed by pouring lead into a pocket provided in available space in the casting that also includes the drive gear for the eccentric. This sometimes results in a counterweight whichJ while counterbalancing the .0 e~fec-ts o~ the eccentric 9 may create other undasirable forces. In additionJ -there appears to be inherent inaccura-cies and complexities in so forming the counterweights.
12;~56~79 Similarly counterweights formed and located as shown in U.S. Patent 1,945,791 have also proved less than ideal for the required purpose. More ls required than merely sticking a weight of proper size in an available space.
`SUMMARY OF T~E INVENTION
Broadly speaking, the present invention provides a cone crusher comprising: frame means; center shaft housing means carried by the frame means; bore means formed in a central portion of the center sh~ft housing means;
center shaft means, disposed in the bore means of the center shaft housing means, movable in an axial direction with respect to the center shaft housing means but rotationally stationary with respect to the center shaft housing means; piston means coacting with the center shaft means for moving the center shaft means in the axial direction; eccentric means rotatably disposed about the center shaft housing means; drlve means connected to the eccentric means to drive same in a predetermined driven direction; crusher head means carried by the center shaft housing means and having skirt means disposed for coaction with the eccentric means such that when the eccentric means is driven by the drive means the crusher head means is gyrated and rotated with respect ~o the eccentric means;
plain bearing means disposed between coacting surfaces of LCM:mls :1~35~
the eccentric means and the skirt means; and roller bearing means disposed between coacting sur~aces of the eccentric means and the center shaft housing means.
Thust this invention involves new and improved cone crushers, of the gyratory type, which incorporate an eccentric, rotatable about a stationary shaft, and which coacts with the depending skirt, of the movable crushing tool support cone, to impart a gyratory motion to the movable crushing tool. The invention contemplates:
providing a combination o~ both plain ~nd roller bearings to mount the eccentric in the cr~usher, and for coaction with the lower crushing tool mounting cone; providing the main thrust bearing assembly, which also serves to support the lower crusher tool mounting cone, with coacting surfaces that facilitate proper and complete lubrication of the bearing; providing a direct .
. ~
~ LCM:mls ~Z356~9 and efficient path o~ lubricant flow to the main thrust bea~ing assembIy for all positions of adjustme~t of the crusher gap; providing lubrication channels and flow patterns that insure proper lubrication of the plain bear-ing, and for that matter lubrication to all bearings that reach the bearing after being ~iltered and cooled and without first passing through other bearings; providing a counterweighted flywheel that is fabricated ko not only offset ~he rotational effect of the eccentric but also with its rotational forces located and distributed to minimize unwanted moments about the center of gravit~ o~ the crusher.
Other ob~ects, features, and advantages of the invention in its details oE construction and arrangement of parts will 1~ be seen from the above; from the following description of the preferred embodiment when considered with the drawing and from the appended claimsO
BRIEF_DESCRIPTION OF-THE DRAWING
In the drawing:
~0 FIG. 1 is a vertical ~levation of a ~piderless gyratory cone crusher, incorporating the instant invention, secti.oned in part and with ~ome parts shown out of rotation to better show details thereof, lZ35679 FIG. 2 is an enlarged view of a portion o the sectioned showing of the crusher of E~IG. 1, FIG. 3 is a further enlargement of a portion of FIG. 2 showing details of some lubrication flow paths, and of other S components o the crusher;
FIG. 4 is a sectional view taken on line 4-4 o FIG. l;
FIG. 5 is a plan view of the ball sector of the main thrust bearing assembly for the cone crusher of FIG. l; and FIG. 6 is a partial sectional view, o the flywheel sub-assembly for the cone crusher, showing the counterweight pouring mold in place during the counterweight forming , process.
I
BRIEF DESCRIPTI0~-OF-THE PREFERRED EMBODIMENT
For convenience, the invention will be described as applied to a spiderless gyratory cone crusher; it being understood, nevertheless, that without departing from the scope of this invention; that the combination plain bearing/roller bearing mounting or the eccentric and
2.0 movable crushing tool; that -the main thrust bearing config-uration, that the lubrication sys-tem for tlle bearings, and especially t~e lubrication system for the plain bearing;
and that the counterweighted flywheel; can all be utilized for other types of cone crushers.
``` ~Z356~
With reference to ~IGo 1 there is shown at 20 a spi~er-less gyratory cone crus~ler the working mechanisrns of which are enclosed in a lower frame assembly 22, and an upper frame assembly 24 provided with a ma~erial infeed opening 26.
An input power drive assembly 30 includes a drive shaft 32, for interconnection by suitable means (such as a drive belt, flywheel and gear box not shown~ to an appropriate source of drive power such as an electric motor or diesel engine (neither being shown~ 9 and a drive pinion 34 for transmittincJ -~he input power ~o a ri~g year 36 of an eccentric`assembly 40.
Eccentric assembly 40 (FIGS. 1 and 2) is rotatably disposed about a fixedly positioned center shaft housing 50 -lS o~ lower frame assembly 22; and for coaction with the inner wall 56 of a depending skirt ~0 of a lower crushing tool mounting cone or crusher head assembly 62 to impaLt a gyratory motion to crusher head assembly 62 and a lower or movable crushing tool or mantle 64 carried thereby. Such 2~ gyratory motion results in crushing of material (not shown) fed through opening ~6 (FI~ as sa;.d material passes through a crushing chamber 70 formed between lower tool 64 ~Z356~9 and an upper crushing tool or concave 72 carried by upper frame assembly 24. An appropriately counterweighted fl~heel assembly 74 (FIGS. 1 and 2~ is also carried ~y eccentric asse~nbly 40.
S Crusher head assembly 62 i5 positioned for its gyratory motion on top of a main thrust bearing assembly 80 carried by a center shaft 82 disposed for vertical movement in a bor~ 84 (FIG. 2) formed in center shaft housing S0. A center shaft piston 86 is disposed at the lower ~nd of center shaft 82 for operation in a hydraulic cylinder 8~ formed at the lower encl of center shaft: ~ousing 50 by way of appropri.ate hydraulic fluid 89 of an accumulator assembly 90 (FIG. 1).
An anti-spin sha~t 92 (FIGS. 1 and 2~ interconnects center shat 82 to an anti-spin assembly 94 disposed within crusher lS head assembly 62~ ¦
~ lubrication assembly 100 (FIG. 1) provides clean and resh lubricant 102 from a reservoir 104 to all bearing surfaces of cone crusher 20 in such a manner that the lubricant for any particular bearing does not previously ~0 pass -through another bearing or bearing surface. Suitable channelways and passages~ to be herelnaEter described, are provided to accomplish this.
More specifically, center shaft housing 50 is fixedly posi~ioned in the bore 110 (FIG~ 1) of a cylinder support ~L~356~9 ring 112 which is an inte~ral part o:E lower housing assembly 22. A cylinarical liner ll~, disposed in a lower enlarged portion 116 of bore 84 to form thexewith hydraullc cylinder 88, is secured in place by an end cap 118 and suitable threaded members 120 and nuts 122~ An appropriate opening 130 is formed in end cap 118 to receive a conduit pipe 132 tFIGS. 1 and 2) of accumulator assembly 90O
Center shafk piston 86 is secured to th~ bottom of center shaft 82 by suitable means such as t.hreaded members 136~ Suitably sized seal rings 138~ disposed in a groove 140 formed at the lower ex~remity of piston 86, are secured in place by a piston end cap 142-which is, in turn, secured in place by threaded members 144a A lower bushing 150 is disposed at the juncture where lower enlarged portion 116 of bore 84 meets the reduced portion thereo~
An upper center shaft bushing 160 ~FIGS. 2 and 3 disposed at -the upper extremity of bore 84 is secured in position by a locking plate 162 and a plurality of threaded members 164. Upper bushing 160 and lower bushing 150 ~0 facilitate the disposikion and ~ertical movement of c~nter ~haft 82 in bore 84 under the hydraulic action of accumulator assembly 90. A pair of keys 165 are ormed in .
locking plate 162 for coaction wit~ suitably formed slots 166 at top of center shaft 82 to prevent rotation o center shat 82 in bore 84; while permitting the vertical movement thereof.
lZ35679 A lubrica-tion passageway 18~ FIGS. 2,3, and 4) i5 drilled down frol~ the top of cente~ shaEt 82 to intersect with a radially extend- ing channel 182~ 'rhe outer extremity of channel 182 is disposed so ~s to be in communication with a vertically extending slot 184, formed in upper bushing 160, for all positions of center shaft 82 in bore 84. A
xadially extending channel 190, also in communication with slot 184, is formed in wall 192~ o~ center shaft housing 50, so as ~o be in communication with a vertical passageway 194 ~ormea in wall 192 and extending to the lower extremity thareo~.
The upper end of lubrication-passageway 180 is disposed to direct lubrication fluid through an aperture 200 ~FIG
2) centrally disposed in socket 201 of main thrust bearing assembly 80. The upper surface of socket 201 is smooth s~lx~aced and of dished configuration and receives a thrust bearing ball sector 202 (FIGS~ 2~ and 5~ also formed with a centrally disposed aperture 204. A plurality o~ circular.
lubrication channels 206 ~FIGo 5~ and radial lubrication cha~mels 208 are formed in the surface of thrust bearing ball sec-tox 2020The relationship between circular lubrication channels 206 and radial lubrication channels 208 is such that every point on the smooth dished upper surface of socket 201 (E~IG~ 2 ) will be Pxposed to a lubrication channel dur.ing 1~3S67~
each cycle of movement of thrus-t bearing ball sector 202 upon socket 201. Such movernent is conventional and well Xnown; but the specific relationship of the lubrication channels as herein descrihed is not. For the movements of ball sector 202 the preferred relationship is that the lubrication passageways be spaced no greater than the distance a point on ball sector 202 will travel during one cycle of rotation of eccentric 40 about center shaft 82;
and a corresponding cycle of gyration of crusher head 62 with respec~ to center shaft 82.
The gyrator~ action of crusher head 62 upon center shaft 82, and of ball sector 202 with respect to socket 201, results from forming the outer surface of eccentric 40 so as to be concentric with an axis of rotation X (FIG. 2) which lS is disposed at a predetermined angle "a" with respect to the vertical axis Y of center post 82. Vertical axis Y is also the axis of rotation of the inner surface of eccentric ~0 about center post housing 50 and center post 82 and, as such, will be hereinafter referred to as the axis of rotation of eccen~ric 40. Axis X and axis Y intersect at a point P whic'n is the center of a sphereO of radius R, used to define the configuration of dished surace of ball socket 201 and the configuration o ~2356'79 the surface of ball sector 202~ It should be understood that while eccentric 40 is verticall~ fixed, that center post 82 and the dished surface of socket 201 do~ in fact, move between a lower position (FIG. 2~ and an upper pOSition (not shown~ depending upon the setting of lower crushing tool 64 with respec-t to upper crushing tool 72.
Radius R is arbitrarily selected for this embodiment to correspond to a setting midway between the two extremes for lower crushing tool 64.
Thus the distance of travel, of ball sector 202 wit~
respect to socket 201 for single cycle of rotation of eccentric ~0 (or gyration of crusher head 62~, when viewed on a vertical plane surface intersecting sector 202 and `
socket 201, can be determined by use of the equation:
D = 2 (R)(tan.9 a) where D is the distance a point on ball sector 202 travels upon the surface of socket 201 for each cycle of gyration of cone 20;
7.0 R is the length of the radius line from an imaginary point P determined by the intersection of the axis of rotation X of the outer surface of eccentric 40 and the axis of rotation Y of eccentric 40 itself;
and lLZ3~
ca is the angle at which the axis X and the axis Y
meet.
The width of eac~n lubrication channel 206, 208 is selected so as to be wide enough to account for the fact the point P is selected as a midpoint ~etween the upper and lower extremities for crusher head 62; while at the same time no~ to be so wide as to unduly diminish the bearing sur~ace o~ ball sector 202.
An additional pair of vertical lubrication passages 220 ` tFIGS~ 2,3, and 4) and 222 ~FIG~ 4~ extend up from the lower extremity of wall 192 of housing 50. Radial lubrication passages 224 tFIGS. 3 and 4) and 226 (FIG. 4) interconnect vertical passages 220, 222 respectively with a groove 234 (FIGS. 3 and 4) formed in and completely encircling an inner sur~ace 236 of eccentric assernbly 40.
A radial channel 238 extends rom groove 234, ~-hrough wall 240 of eccentric 40, to an outer surface 242 thereof.
More particularly radial channel 238 intersects outer sur~ace 242 oE eccentric 40 at a predetermined location "L"
~235679 with res~ect to t~e location M (FIG. 4) of maximum load on eccentric 40. In this particular instance location "L" pre-cedes location ~l (in the direction of rotation of eccen-tric 40 under load ... i.e. counterclockwise in FIG. 4) by S approxirnately 120. The maximurn load location M for the described embodiment, in turn, precedes that part of eccen-tric 40 with the thickest wall dimension, location "T", by approximately 15. Alternatively location "L" can be described as trailing that part of eccentric 40 with -the thinnest wall dimension location, "S", by approximately 45.
~owever, it is important to note that the maximum load location M may occur between 15 and 45 from (preceeding) location "T" depending upon the degree of fineness or courseness of the output product from crusher 20. The placement of location L for radial channel 238 will, however, always be approximately 120~ from location M.
A flat 244 (FIGS. 3 and 4), of predetermined extent8 is formed on outer.surface 242 of eccentric 40 to facilitate collection of lubrication fluid 102 proxlmate location ~. In .0 thi~ particular instance flat 244 spans an arc of approxi-mately 20~ As shown in FIG~ 3 flat 244 i5 bounded at its upper extremity by an edge 246 and at its lower e*tremity by an edge 248, each of which results from the orming of fla-t 244 on outer surface 242. As eccentric 40 rotates lubrica~
ting oil 102 reaching location L will be wiped over .inner ~2356~9 wall 56 of skirt 60 of crusher head 62 and upon the opposing outer surface of eccentric 40, as will be explained in more detail hereinafter.
It should be noted that ou-ter surface 242 of eccentric 40 constitutes a plain bearing 252 (FIGS. 2 and 3) in its relationship with inner wall 56 of skirt 60 of crusher head 62. Accordingly, suitable bearing material such as babbitt metal 254 is disposed in appropriate thickness on ou-ter surface 242, inciuding flat 244 thereof. Babbitt metal 254, however, does not cover the entire vertical extent of surface 242 but instead ex~ends from proximate the upper extremity thereof to a predetermined location 256 above a lower extremity 257 of eccentric 40. That predetermined location depends upon the height of eccentric 40, the co-extensive areas of wall 56 of skirt 60 and of outer surface 242, and most important the vertical distance of outer surface 242 that will be exposed from skirt 60 when center shaft 82 and crusher head 62 are raised to their highest position.
Babbitt 254 wears as skirt 60 and eccentric 40 coact. If a lower edge 260 of skirt 60 is raised to a point higher than lower edge 256 of babbitt metal 254 then, the wear on babbitt metal 254 will be uneven possibly causing premature bearing failure.
~3S6~g An upper roller bearing as~embly 261 (FIGS. 2 and 33 seated in an upper bea.ri.ng groove 262 forrned i~ the upper extremity of inner su~ace 236 of eccentric 40~ completely encircles center posk ~lousing 50 and is encircled by eccentric 40~ An upper bearing retainer assernbly 264 secures upper hearincJ assembly 261 in position.
A lower roller bearing assembly 270, seated in a lower bearing groove 272 formed at t'ne lower ex-tremity of inner surface 236 of eccentric 40, also completely encircles center post housing 50 and is encircled by eccentric 400 Ring gear 36 ~ecures :Lower bearing 270 in position.
Circumferentially disposed about the periphery of eccentric 40, and appropriately secured thereto, is fabri-cated ~lywheel assembly.74 (FIGS. 2,3, and 4). Flywheel assembly 74 includes components for sealing out dirt and dust from plan bearing 252 and roller bearing assemblies 261 and 270; and is built up by securing an appropriately sized annular ring 276 (FIG. 3) to a horizontally extending shoulder 278 of eccentric 40 as by threaded members 280. A
2.0 lower cylinder 282 is secured to and extends upwardly from ring 2-/6. An upper annular riny ~84 is fixedly disposed at the upper extremity of cylinder 282~ A pair of gruoves 286 formed in the lower surface of upper ring 284 mate with a ~17~
~L23567~
pair of annular ribs 290 formed on top of vertical wall 292 of lower housing assembly 22 to form therewi-th a labyrinth type dust seal when filled with an appropriate grease. An upper cylinder 300 is secured to and extends upwardly from upper ring 284. One or more upper grooves 301 are formed proximate the upper end of cylinder 300, each so as to receive seal rings 302, which in turn extend out under their own spring action into engagement with an inner surface 303 of a cylindrical ring 304 extending from crusher head assembly 62; this arrangement seals out dust and dirt while allowing vertical adjustment and move-ments'of crusher head 62.
An inner surface 305 (FIGS. 2 and 3) of lower cylinder 282 is machined at an appropriate angle so that any lubricating oil 102, which may fall upon surface 305, will be induced by the centrifugal action of rotating flywheel 74 to flow downwardly and through a plurality of relatively large openings 306 formed through, and all around, annular ring 276. A shield 307 (FIGS.
2 and 4) is secured to an upper surface of upper annular ring 284 to minimize upward splashing of any lubricating oil 102 which may be near cylinder 282. Shield 307 extends only part way around cylinder 282 (FIG. 4) and widens in radial dimension as it ~23s67g approaches its ends; all so that a clearance space is pro-vided between shield 307 and the outer surface of skirt 60 as crusher head 62 gyratesO
The coaction of seal ring 302 upon .inner surface 303 of S ring 304, to provide an effective seal, is accomplished by disposing upper cylinder 300 upon upper annular ring 284 so that the axis of rotation of upper cylinder 300 corresponds to axis of rotation "X" (FIGS. 2 and 5~ of outer surface 242 of eccentric 4Q; whileJ at the same time, the axis of rotation of lower cylinder 282 corresponds to axis of rotation Y of eccentric 40~
A counterweight 308 (FIGS. 2 and 6) is formed against inner surface of cylinders 282, 300 of a size and disposi-tion to offset the unbalance forces induced by rotating eccentric 40 and all other gyrating parts within cone crusher 20; such as crusher head 62. In the formation of counterweig~t 308 it is i~portant to distribute its weight so that as it rotates, with flywheel 74, any tendency to generate further unbalance forcesO or couples~ with respect .0 to the forces generated by the gyrati.ng parts 3 are minimized. This is accomplished by providing a configura-tion for counterweight 308 that places its center of gravity --19-- ' ~L~35679 and a line perpendicular to axis Y that is as close as possible to a similar line upon which the center of gravity of the gyrating parts would fall. Preferably th0 two centers of gravity should be on a single line that is pexpendicular to axis Y.
Counterweight 308 is formed by pouring a dense material in situ, during the manufacture of a sub-assembly which includes lower annular ring 276, lower cylinder 282, upper annular ring 284, and upper cylinder 300; and before shield 307 is in~talled or the sub-assembly is secured to shoulder 278 of eccentric 40. A plurality of L shaped lugs 309 (FIGS.
4 and 6) are disposed abou~ the inner surfaces o cylinders 282, 300, in the area thereof where counterweight 308 is to be poured. ~ne leg of each lug 309 is secured, as by welding to its respective inner surface; while the other leg of lug 309 extends laterally therefrom to be embedded into the poured dense material to ~acilitate holding counterweight 308 in place.
A pourin~ mold 310 (FIG~ 6~ is utili~ed to facilitate ~0 the pouring and molding process for counterweight 308.
Pouring mold 310 includes a base plate 311, that is secured ~Z3S67~
to ring 276 by a plurality of bolts 312 (only one s'nown~, and a mold plate assembly 313 that is secured to base plate 311 by a plurality of bolts 314 (only one shown). Suitable locating pins (not shown) extend from mold plate assembly 313 and/or base plate 311 to co-operate with holes (not shown) formed in ring 276 to facilitate locating pouring mold 310 in the sub-assembly of FIG. 6. Thereafter end pieces of mold plate assembly 313 are placed to abut inner surfaces of cylinders 282 and 300 respec.tively. Once 1~ pouriny molcl 310 is so disposed a pocke~ 315 is formed in the space above ring 276 and between inner surfaces of cylinders 282, 300 and an inner surface 316 of mold plate assembly 313. Inner surface 316 is formed so that counter-weight 308 will hve an exposed lower surface 317 which is substantially parallel to inner surface 305 of lower cylinder 282 so that lubricating oil 102 will flow out through openings 306 of ring 276 under centrifugal action of rotating flywheel 74. Inner surface 316 is further formed so that counterw~ight 308 will have an exposed upper .0 surface 318 that is substantially parallel to axis Y, ~nd an exposed intermediate area 319 that extends towards skirt 60, when flywheel 74 is assembled to eccentric 40, sufici-ently to permit the gyrating movement of skirt 60 but, like shield 307, close enough ~o rninimize splashing of oil 102 above t~is position, Prior to pouring the dense material .into pocket 315 a suitable packing material 320 ~FIG. 6) such as an asbestos S type material, is placed in-to each opening 306 within pocket 315 to prevent such opening 306 from being filled with the dense material. It should be noted that openings 306 proximàte the position of counterweight 308 are formed opposite in position to those on the other side of ring 276 . (as shown in FIG~ 4) and so -that -the~ extend past a lower extremity of counterweight 308 50 that oil 102 flows beneath counterweight 308 and through such openings 306.
With pouring mold 310 in place and appropriate openings 306 filled with packing 320 a suita'~le dense material, such ` as lead, is poured into pocket 3150 After t'ne lead hardens pouring mold 310 and packing 320 are removed, and flywheel 74 with counterweight 308 can be assembled to eccentric 40.
T'h'e size of pouring mold 310, and its disposition with xespèct to the sub-assernbly is selected so that the ~0 res~lltant counterweight 308 will be of the correct weight nncl will be positioned as herein'be~ore described.
~235679 An alternative method of forming a counterweight i5 shown in FIG. 4 wherein an inner wall 321 is secured to annular ring 276 (FI~S. 3 and 7~ so as to extend upwardly theref~om and s~ as to be ~paced a predetermined distance in~ardly from the inner walls of lower cylinder 282 and upper cylinder 300. Inner wall 321 is substantially concentric with walls 282, 300 but is inclined generally outwardly from wall 282 as it rises up from annular ring 276. The incline is selected to facilitate the flow o~ oil 102 ~hrough opening 306. Inner wall 32l. is spaced froJn the outer surface of wall 240 of eccentric 40 a distance suf~icient to accommodate gyrating skirt 60 of crusher head assembly 62 therebetween.
End plates 322, 324 (FIG, 7) connect the extremities of lS inner wall 321 to walls 2820 300 to form between ~alls 282 300, 321, 322, 324 and above annular r;ng 2i6 a pocket 326 (FIG. 7) that is opèn at the top. Lead 328 is poured into pocket 326 to form therein a counterwe;ght 330; the amount o~ lead and its positioning due to walls, 3210 322, and 324 2.0 being selected to balance and o~set the rotative forces developed by eccentric 40. Countarweight 330 is si~ed in .-23-123~6~9 height so that the forces it generates, as flywheel 74 rotates, will be substantially evenly distributed with respect to the center of gravity of crusher 20.
The remaining surfaces of the flywheel of FIG. 7 are as previously described with respect to FIG. 2.
A plurality of drain channels 332, 334, 336, 338 (FIG. 4) extend down from the upper extremity of skirt 60 through the lower extremity thereof to provide a return flow path for lubrication oil 102 through drain holes 306 of annular ring 276, into lower housing 22 of crusher 20.
A drain 342 (FIGS. 1 and 2) provides a means of exit for oil 102 from within housing 22 to an oil return pipe 344 (FIG. 1) and then to oil reservoir 104. Reservoir 104 is conventionally equipped with suitable filters (not shown) and cooling equipment to filter and cool oil 102.
A pump 350 is suitably connected to reservoir 104 to with-draw oil 102 therefrom and to pump oil 102 through a relief valve 352, a flow meter 354, suitable piping 356, a flow divider 358, and lube conduits 360, 362 and 364. Conduit 360 is ~ connected, by suitable couplings, to lubrication passages 220, 222; while conduit 362 is connected by a suitable coupling, to lubrication passage 194. Pump 350 is suitably connected to a source of electrical or other motive power; and is otherwise provided with appropriate controls and monitoring devices. Flow divider 358 divides the flow J~....
123567~
o~ oil 102 so that one third of the oil flows into conduit 362 and two-thirds of oil 102 flow into concluit 360.
Prior to crushing rock or like ma-terial with crusher 20; and a~ter crusher 20 has otherwise been prepared to crush rock it is essential that lubrication oil 102 be pumped throughout crusher 20 to al:l. its bearings and other surfaces which are to be lubricated. Pump 350 is started and oil 102 from reservoir 104 is pumped through filter 352, flow meter 354, pipe 356, flow divider 358 and lube conduits 360 and 362. The :Elow paths for oil 102 are indicated by the arrows in FIGS. 2 and 3O
Oil 102 flowing through conduit 362 is pumped up vertical lubrication passage 194 (FIG. 3), out radial channel 190, through slot 184, through radial channel 182, up vertical passageway 180, through aperture 200 -in main thrust bearing socket 201, and through aperture 204 in main thrust ball sector 202 to fill the space around main thrust bearing assembly 80. Oil 102 will fill lubrication channels 206,. 208 o ball sector 202 and spill out the periphery ~?.0 thereof.to fall into the space around the upper portion of eccentric 40 and from there through drain channels 332~
334, 336 and 338 of skirt 60. Thereafter oil 102 returns through openings 306, drain plug 342, and return pipe 344 -to reservoir 104.
:~Z356~
Oil 102 flowing throug'n conduits 360 is pump~d up passageways 220, 222 and out radi.al channels 224, 226 .into circular groove 234, Oil flowing Erom groove 234 flows -through an appropriately sized space hetween inner wall 236 o eccentric 40 and the outer wall of center shaft housing 50 to lubricate roller bearing assemblies 261, 270. Oil 102 flowing through upper bearing assembly 261 exits through drain channels 360, 362, 364, 366 and then through openings 306; and from lower bearing assembly 270 oil 102 flows directly out through openings 306.
An appropriate por-tion of oil 102 i5 pumped through radial channel 238 to flat 244 where it is ~Jiped upon the surfaces of babbit metal 254 and opposing inner surface 56 of skirt 60. This oil 102 is then pumped up over the edge of 1~ babbit metal 254 and down past bottom edge 256 thereof by the coaction of eccentric 40 and skirt 60~ The used oil 102 flows out through openings 306 and thence bac~ to reservoir 104.
It should thus be obvious that none of the oil 102 is .0 pumped -~o a second bearing or bearing surface after being -26~
i~356~9 used to lubricate a ~irst bearing or bearing surface; and that oil 102 to be received by any ~earing or bearing surface is relatively cool and filtered~
The lower frame assembly, the upper frame assembly~
S input drive, accumulator and other components and mec'nan-isms required to render the cone crusher operative are constructed, arranged, and operated in the manner similar to comparable assembly, mechanisms and components described in U.S. Patent 4,168,036.
It is understood that although I have shown the pre-ferred embodiments of my invention that various modifica-tions ma~ be made in details thereof without departing from the spirit as comprehended by the following claims.
~ , .
and that the counterweighted flywheel; can all be utilized for other types of cone crushers.
``` ~Z356~
With reference to ~IGo 1 there is shown at 20 a spi~er-less gyratory cone crus~ler the working mechanisrns of which are enclosed in a lower frame assembly 22, and an upper frame assembly 24 provided with a ma~erial infeed opening 26.
An input power drive assembly 30 includes a drive shaft 32, for interconnection by suitable means (such as a drive belt, flywheel and gear box not shown~ to an appropriate source of drive power such as an electric motor or diesel engine (neither being shown~ 9 and a drive pinion 34 for transmittincJ -~he input power ~o a ri~g year 36 of an eccentric`assembly 40.
Eccentric assembly 40 (FIGS. 1 and 2) is rotatably disposed about a fixedly positioned center shaft housing 50 -lS o~ lower frame assembly 22; and for coaction with the inner wall 56 of a depending skirt ~0 of a lower crushing tool mounting cone or crusher head assembly 62 to impaLt a gyratory motion to crusher head assembly 62 and a lower or movable crushing tool or mantle 64 carried thereby. Such 2~ gyratory motion results in crushing of material (not shown) fed through opening ~6 (FI~ as sa;.d material passes through a crushing chamber 70 formed between lower tool 64 ~Z356~9 and an upper crushing tool or concave 72 carried by upper frame assembly 24. An appropriately counterweighted fl~heel assembly 74 (FIGS. 1 and 2~ is also carried ~y eccentric asse~nbly 40.
S Crusher head assembly 62 i5 positioned for its gyratory motion on top of a main thrust bearing assembly 80 carried by a center shaft 82 disposed for vertical movement in a bor~ 84 (FIG. 2) formed in center shaft housing S0. A center shaft piston 86 is disposed at the lower ~nd of center shaft 82 for operation in a hydraulic cylinder 8~ formed at the lower encl of center shaft: ~ousing 50 by way of appropri.ate hydraulic fluid 89 of an accumulator assembly 90 (FIG. 1).
An anti-spin sha~t 92 (FIGS. 1 and 2~ interconnects center shat 82 to an anti-spin assembly 94 disposed within crusher lS head assembly 62~ ¦
~ lubrication assembly 100 (FIG. 1) provides clean and resh lubricant 102 from a reservoir 104 to all bearing surfaces of cone crusher 20 in such a manner that the lubricant for any particular bearing does not previously ~0 pass -through another bearing or bearing surface. Suitable channelways and passages~ to be herelnaEter described, are provided to accomplish this.
More specifically, center shaft housing 50 is fixedly posi~ioned in the bore 110 (FIG~ 1) of a cylinder support ~L~356~9 ring 112 which is an inte~ral part o:E lower housing assembly 22. A cylinarical liner ll~, disposed in a lower enlarged portion 116 of bore 84 to form thexewith hydraullc cylinder 88, is secured in place by an end cap 118 and suitable threaded members 120 and nuts 122~ An appropriate opening 130 is formed in end cap 118 to receive a conduit pipe 132 tFIGS. 1 and 2) of accumulator assembly 90O
Center shafk piston 86 is secured to th~ bottom of center shaft 82 by suitable means such as t.hreaded members 136~ Suitably sized seal rings 138~ disposed in a groove 140 formed at the lower ex~remity of piston 86, are secured in place by a piston end cap 142-which is, in turn, secured in place by threaded members 144a A lower bushing 150 is disposed at the juncture where lower enlarged portion 116 of bore 84 meets the reduced portion thereo~
An upper center shaft bushing 160 ~FIGS. 2 and 3 disposed at -the upper extremity of bore 84 is secured in position by a locking plate 162 and a plurality of threaded members 164. Upper bushing 160 and lower bushing 150 ~0 facilitate the disposikion and ~ertical movement of c~nter ~haft 82 in bore 84 under the hydraulic action of accumulator assembly 90. A pair of keys 165 are ormed in .
locking plate 162 for coaction wit~ suitably formed slots 166 at top of center shaft 82 to prevent rotation o center shat 82 in bore 84; while permitting the vertical movement thereof.
lZ35679 A lubrica-tion passageway 18~ FIGS. 2,3, and 4) i5 drilled down frol~ the top of cente~ shaEt 82 to intersect with a radially extend- ing channel 182~ 'rhe outer extremity of channel 182 is disposed so ~s to be in communication with a vertically extending slot 184, formed in upper bushing 160, for all positions of center shaft 82 in bore 84. A
xadially extending channel 190, also in communication with slot 184, is formed in wall 192~ o~ center shaft housing 50, so as ~o be in communication with a vertical passageway 194 ~ormea in wall 192 and extending to the lower extremity thareo~.
The upper end of lubrication-passageway 180 is disposed to direct lubrication fluid through an aperture 200 ~FIG
2) centrally disposed in socket 201 of main thrust bearing assembly 80. The upper surface of socket 201 is smooth s~lx~aced and of dished configuration and receives a thrust bearing ball sector 202 (FIGS~ 2~ and 5~ also formed with a centrally disposed aperture 204. A plurality o~ circular.
lubrication channels 206 ~FIGo 5~ and radial lubrication cha~mels 208 are formed in the surface of thrust bearing ball sec-tox 2020The relationship between circular lubrication channels 206 and radial lubrication channels 208 is such that every point on the smooth dished upper surface of socket 201 (E~IG~ 2 ) will be Pxposed to a lubrication channel dur.ing 1~3S67~
each cycle of movement of thrus-t bearing ball sector 202 upon socket 201. Such movernent is conventional and well Xnown; but the specific relationship of the lubrication channels as herein descrihed is not. For the movements of ball sector 202 the preferred relationship is that the lubrication passageways be spaced no greater than the distance a point on ball sector 202 will travel during one cycle of rotation of eccentric 40 about center shaft 82;
and a corresponding cycle of gyration of crusher head 62 with respec~ to center shaft 82.
The gyrator~ action of crusher head 62 upon center shaft 82, and of ball sector 202 with respect to socket 201, results from forming the outer surface of eccentric 40 so as to be concentric with an axis of rotation X (FIG. 2) which lS is disposed at a predetermined angle "a" with respect to the vertical axis Y of center post 82. Vertical axis Y is also the axis of rotation of the inner surface of eccentric ~0 about center post housing 50 and center post 82 and, as such, will be hereinafter referred to as the axis of rotation of eccen~ric 40. Axis X and axis Y intersect at a point P whic'n is the center of a sphereO of radius R, used to define the configuration of dished surace of ball socket 201 and the configuration o ~2356'79 the surface of ball sector 202~ It should be understood that while eccentric 40 is verticall~ fixed, that center post 82 and the dished surface of socket 201 do~ in fact, move between a lower position (FIG. 2~ and an upper pOSition (not shown~ depending upon the setting of lower crushing tool 64 with respec-t to upper crushing tool 72.
Radius R is arbitrarily selected for this embodiment to correspond to a setting midway between the two extremes for lower crushing tool 64.
Thus the distance of travel, of ball sector 202 wit~
respect to socket 201 for single cycle of rotation of eccentric ~0 (or gyration of crusher head 62~, when viewed on a vertical plane surface intersecting sector 202 and `
socket 201, can be determined by use of the equation:
D = 2 (R)(tan.9 a) where D is the distance a point on ball sector 202 travels upon the surface of socket 201 for each cycle of gyration of cone 20;
7.0 R is the length of the radius line from an imaginary point P determined by the intersection of the axis of rotation X of the outer surface of eccentric 40 and the axis of rotation Y of eccentric 40 itself;
and lLZ3~
ca is the angle at which the axis X and the axis Y
meet.
The width of eac~n lubrication channel 206, 208 is selected so as to be wide enough to account for the fact the point P is selected as a midpoint ~etween the upper and lower extremities for crusher head 62; while at the same time no~ to be so wide as to unduly diminish the bearing sur~ace o~ ball sector 202.
An additional pair of vertical lubrication passages 220 ` tFIGS~ 2,3, and 4) and 222 ~FIG~ 4~ extend up from the lower extremity of wall 192 of housing 50. Radial lubrication passages 224 tFIGS. 3 and 4) and 226 (FIG. 4) interconnect vertical passages 220, 222 respectively with a groove 234 (FIGS. 3 and 4) formed in and completely encircling an inner sur~ace 236 of eccentric assernbly 40.
A radial channel 238 extends rom groove 234, ~-hrough wall 240 of eccentric 40, to an outer surface 242 thereof.
More particularly radial channel 238 intersects outer sur~ace 242 oE eccentric 40 at a predetermined location "L"
~235679 with res~ect to t~e location M (FIG. 4) of maximum load on eccentric 40. In this particular instance location "L" pre-cedes location ~l (in the direction of rotation of eccen-tric 40 under load ... i.e. counterclockwise in FIG. 4) by S approxirnately 120. The maximurn load location M for the described embodiment, in turn, precedes that part of eccen-tric 40 with the thickest wall dimension, location "T", by approximately 15. Alternatively location "L" can be described as trailing that part of eccentric 40 with -the thinnest wall dimension location, "S", by approximately 45.
~owever, it is important to note that the maximum load location M may occur between 15 and 45 from (preceeding) location "T" depending upon the degree of fineness or courseness of the output product from crusher 20. The placement of location L for radial channel 238 will, however, always be approximately 120~ from location M.
A flat 244 (FIGS. 3 and 4), of predetermined extent8 is formed on outer.surface 242 of eccentric 40 to facilitate collection of lubrication fluid 102 proxlmate location ~. In .0 thi~ particular instance flat 244 spans an arc of approxi-mately 20~ As shown in FIG~ 3 flat 244 i5 bounded at its upper extremity by an edge 246 and at its lower e*tremity by an edge 248, each of which results from the orming of fla-t 244 on outer surface 242. As eccentric 40 rotates lubrica~
ting oil 102 reaching location L will be wiped over .inner ~2356~9 wall 56 of skirt 60 of crusher head 62 and upon the opposing outer surface of eccentric 40, as will be explained in more detail hereinafter.
It should be noted that ou-ter surface 242 of eccentric 40 constitutes a plain bearing 252 (FIGS. 2 and 3) in its relationship with inner wall 56 of skirt 60 of crusher head 62. Accordingly, suitable bearing material such as babbitt metal 254 is disposed in appropriate thickness on ou-ter surface 242, inciuding flat 244 thereof. Babbitt metal 254, however, does not cover the entire vertical extent of surface 242 but instead ex~ends from proximate the upper extremity thereof to a predetermined location 256 above a lower extremity 257 of eccentric 40. That predetermined location depends upon the height of eccentric 40, the co-extensive areas of wall 56 of skirt 60 and of outer surface 242, and most important the vertical distance of outer surface 242 that will be exposed from skirt 60 when center shaft 82 and crusher head 62 are raised to their highest position.
Babbitt 254 wears as skirt 60 and eccentric 40 coact. If a lower edge 260 of skirt 60 is raised to a point higher than lower edge 256 of babbitt metal 254 then, the wear on babbitt metal 254 will be uneven possibly causing premature bearing failure.
~3S6~g An upper roller bearing as~embly 261 (FIGS. 2 and 33 seated in an upper bea.ri.ng groove 262 forrned i~ the upper extremity of inner su~ace 236 of eccentric 40~ completely encircles center posk ~lousing 50 and is encircled by eccentric 40~ An upper bearing retainer assernbly 264 secures upper hearincJ assembly 261 in position.
A lower roller bearing assembly 270, seated in a lower bearing groove 272 formed at t'ne lower ex-tremity of inner surface 236 of eccentric 40, also completely encircles center post housing 50 and is encircled by eccentric 400 Ring gear 36 ~ecures :Lower bearing 270 in position.
Circumferentially disposed about the periphery of eccentric 40, and appropriately secured thereto, is fabri-cated ~lywheel assembly.74 (FIGS. 2,3, and 4). Flywheel assembly 74 includes components for sealing out dirt and dust from plan bearing 252 and roller bearing assemblies 261 and 270; and is built up by securing an appropriately sized annular ring 276 (FIG. 3) to a horizontally extending shoulder 278 of eccentric 40 as by threaded members 280. A
2.0 lower cylinder 282 is secured to and extends upwardly from ring 2-/6. An upper annular riny ~84 is fixedly disposed at the upper extremity of cylinder 282~ A pair of gruoves 286 formed in the lower surface of upper ring 284 mate with a ~17~
~L23567~
pair of annular ribs 290 formed on top of vertical wall 292 of lower housing assembly 22 to form therewi-th a labyrinth type dust seal when filled with an appropriate grease. An upper cylinder 300 is secured to and extends upwardly from upper ring 284. One or more upper grooves 301 are formed proximate the upper end of cylinder 300, each so as to receive seal rings 302, which in turn extend out under their own spring action into engagement with an inner surface 303 of a cylindrical ring 304 extending from crusher head assembly 62; this arrangement seals out dust and dirt while allowing vertical adjustment and move-ments'of crusher head 62.
An inner surface 305 (FIGS. 2 and 3) of lower cylinder 282 is machined at an appropriate angle so that any lubricating oil 102, which may fall upon surface 305, will be induced by the centrifugal action of rotating flywheel 74 to flow downwardly and through a plurality of relatively large openings 306 formed through, and all around, annular ring 276. A shield 307 (FIGS.
2 and 4) is secured to an upper surface of upper annular ring 284 to minimize upward splashing of any lubricating oil 102 which may be near cylinder 282. Shield 307 extends only part way around cylinder 282 (FIG. 4) and widens in radial dimension as it ~23s67g approaches its ends; all so that a clearance space is pro-vided between shield 307 and the outer surface of skirt 60 as crusher head 62 gyratesO
The coaction of seal ring 302 upon .inner surface 303 of S ring 304, to provide an effective seal, is accomplished by disposing upper cylinder 300 upon upper annular ring 284 so that the axis of rotation of upper cylinder 300 corresponds to axis of rotation "X" (FIGS. 2 and 5~ of outer surface 242 of eccentric 4Q; whileJ at the same time, the axis of rotation of lower cylinder 282 corresponds to axis of rotation Y of eccentric 40~
A counterweight 308 (FIGS. 2 and 6) is formed against inner surface of cylinders 282, 300 of a size and disposi-tion to offset the unbalance forces induced by rotating eccentric 40 and all other gyrating parts within cone crusher 20; such as crusher head 62. In the formation of counterweig~t 308 it is i~portant to distribute its weight so that as it rotates, with flywheel 74, any tendency to generate further unbalance forcesO or couples~ with respect .0 to the forces generated by the gyrati.ng parts 3 are minimized. This is accomplished by providing a configura-tion for counterweight 308 that places its center of gravity --19-- ' ~L~35679 and a line perpendicular to axis Y that is as close as possible to a similar line upon which the center of gravity of the gyrating parts would fall. Preferably th0 two centers of gravity should be on a single line that is pexpendicular to axis Y.
Counterweight 308 is formed by pouring a dense material in situ, during the manufacture of a sub-assembly which includes lower annular ring 276, lower cylinder 282, upper annular ring 284, and upper cylinder 300; and before shield 307 is in~talled or the sub-assembly is secured to shoulder 278 of eccentric 40. A plurality of L shaped lugs 309 (FIGS.
4 and 6) are disposed abou~ the inner surfaces o cylinders 282, 300, in the area thereof where counterweight 308 is to be poured. ~ne leg of each lug 309 is secured, as by welding to its respective inner surface; while the other leg of lug 309 extends laterally therefrom to be embedded into the poured dense material to ~acilitate holding counterweight 308 in place.
A pourin~ mold 310 (FIG~ 6~ is utili~ed to facilitate ~0 the pouring and molding process for counterweight 308.
Pouring mold 310 includes a base plate 311, that is secured ~Z3S67~
to ring 276 by a plurality of bolts 312 (only one s'nown~, and a mold plate assembly 313 that is secured to base plate 311 by a plurality of bolts 314 (only one shown). Suitable locating pins (not shown) extend from mold plate assembly 313 and/or base plate 311 to co-operate with holes (not shown) formed in ring 276 to facilitate locating pouring mold 310 in the sub-assembly of FIG. 6. Thereafter end pieces of mold plate assembly 313 are placed to abut inner surfaces of cylinders 282 and 300 respec.tively. Once 1~ pouriny molcl 310 is so disposed a pocke~ 315 is formed in the space above ring 276 and between inner surfaces of cylinders 282, 300 and an inner surface 316 of mold plate assembly 313. Inner surface 316 is formed so that counter-weight 308 will hve an exposed lower surface 317 which is substantially parallel to inner surface 305 of lower cylinder 282 so that lubricating oil 102 will flow out through openings 306 of ring 276 under centrifugal action of rotating flywheel 74. Inner surface 316 is further formed so that counterw~ight 308 will have an exposed upper .0 surface 318 that is substantially parallel to axis Y, ~nd an exposed intermediate area 319 that extends towards skirt 60, when flywheel 74 is assembled to eccentric 40, sufici-ently to permit the gyrating movement of skirt 60 but, like shield 307, close enough ~o rninimize splashing of oil 102 above t~is position, Prior to pouring the dense material .into pocket 315 a suitable packing material 320 ~FIG. 6) such as an asbestos S type material, is placed in-to each opening 306 within pocket 315 to prevent such opening 306 from being filled with the dense material. It should be noted that openings 306 proximàte the position of counterweight 308 are formed opposite in position to those on the other side of ring 276 . (as shown in FIG~ 4) and so -that -the~ extend past a lower extremity of counterweight 308 50 that oil 102 flows beneath counterweight 308 and through such openings 306.
With pouring mold 310 in place and appropriate openings 306 filled with packing 320 a suita'~le dense material, such ` as lead, is poured into pocket 3150 After t'ne lead hardens pouring mold 310 and packing 320 are removed, and flywheel 74 with counterweight 308 can be assembled to eccentric 40.
T'h'e size of pouring mold 310, and its disposition with xespèct to the sub-assernbly is selected so that the ~0 res~lltant counterweight 308 will be of the correct weight nncl will be positioned as herein'be~ore described.
~235679 An alternative method of forming a counterweight i5 shown in FIG. 4 wherein an inner wall 321 is secured to annular ring 276 (FI~S. 3 and 7~ so as to extend upwardly theref~om and s~ as to be ~paced a predetermined distance in~ardly from the inner walls of lower cylinder 282 and upper cylinder 300. Inner wall 321 is substantially concentric with walls 282, 300 but is inclined generally outwardly from wall 282 as it rises up from annular ring 276. The incline is selected to facilitate the flow o~ oil 102 ~hrough opening 306. Inner wall 32l. is spaced froJn the outer surface of wall 240 of eccentric 40 a distance suf~icient to accommodate gyrating skirt 60 of crusher head assembly 62 therebetween.
End plates 322, 324 (FIG, 7) connect the extremities of lS inner wall 321 to walls 2820 300 to form between ~alls 282 300, 321, 322, 324 and above annular r;ng 2i6 a pocket 326 (FIG. 7) that is opèn at the top. Lead 328 is poured into pocket 326 to form therein a counterwe;ght 330; the amount o~ lead and its positioning due to walls, 3210 322, and 324 2.0 being selected to balance and o~set the rotative forces developed by eccentric 40. Countarweight 330 is si~ed in .-23-123~6~9 height so that the forces it generates, as flywheel 74 rotates, will be substantially evenly distributed with respect to the center of gravity of crusher 20.
The remaining surfaces of the flywheel of FIG. 7 are as previously described with respect to FIG. 2.
A plurality of drain channels 332, 334, 336, 338 (FIG. 4) extend down from the upper extremity of skirt 60 through the lower extremity thereof to provide a return flow path for lubrication oil 102 through drain holes 306 of annular ring 276, into lower housing 22 of crusher 20.
A drain 342 (FIGS. 1 and 2) provides a means of exit for oil 102 from within housing 22 to an oil return pipe 344 (FIG. 1) and then to oil reservoir 104. Reservoir 104 is conventionally equipped with suitable filters (not shown) and cooling equipment to filter and cool oil 102.
A pump 350 is suitably connected to reservoir 104 to with-draw oil 102 therefrom and to pump oil 102 through a relief valve 352, a flow meter 354, suitable piping 356, a flow divider 358, and lube conduits 360, 362 and 364. Conduit 360 is ~ connected, by suitable couplings, to lubrication passages 220, 222; while conduit 362 is connected by a suitable coupling, to lubrication passage 194. Pump 350 is suitably connected to a source of electrical or other motive power; and is otherwise provided with appropriate controls and monitoring devices. Flow divider 358 divides the flow J~....
123567~
o~ oil 102 so that one third of the oil flows into conduit 362 and two-thirds of oil 102 flow into concluit 360.
Prior to crushing rock or like ma-terial with crusher 20; and a~ter crusher 20 has otherwise been prepared to crush rock it is essential that lubrication oil 102 be pumped throughout crusher 20 to al:l. its bearings and other surfaces which are to be lubricated. Pump 350 is started and oil 102 from reservoir 104 is pumped through filter 352, flow meter 354, pipe 356, flow divider 358 and lube conduits 360 and 362. The :Elow paths for oil 102 are indicated by the arrows in FIGS. 2 and 3O
Oil 102 flowing through conduit 362 is pumped up vertical lubrication passage 194 (FIG. 3), out radial channel 190, through slot 184, through radial channel 182, up vertical passageway 180, through aperture 200 -in main thrust bearing socket 201, and through aperture 204 in main thrust ball sector 202 to fill the space around main thrust bearing assembly 80. Oil 102 will fill lubrication channels 206,. 208 o ball sector 202 and spill out the periphery ~?.0 thereof.to fall into the space around the upper portion of eccentric 40 and from there through drain channels 332~
334, 336 and 338 of skirt 60. Thereafter oil 102 returns through openings 306, drain plug 342, and return pipe 344 -to reservoir 104.
:~Z356~
Oil 102 flowing throug'n conduits 360 is pump~d up passageways 220, 222 and out radi.al channels 224, 226 .into circular groove 234, Oil flowing Erom groove 234 flows -through an appropriately sized space hetween inner wall 236 o eccentric 40 and the outer wall of center shaft housing 50 to lubricate roller bearing assemblies 261, 270. Oil 102 flowing through upper bearing assembly 261 exits through drain channels 360, 362, 364, 366 and then through openings 306; and from lower bearing assembly 270 oil 102 flows directly out through openings 306.
An appropriate por-tion of oil 102 i5 pumped through radial channel 238 to flat 244 where it is ~Jiped upon the surfaces of babbit metal 254 and opposing inner surface 56 of skirt 60. This oil 102 is then pumped up over the edge of 1~ babbit metal 254 and down past bottom edge 256 thereof by the coaction of eccentric 40 and skirt 60~ The used oil 102 flows out through openings 306 and thence bac~ to reservoir 104.
It should thus be obvious that none of the oil 102 is .0 pumped -~o a second bearing or bearing surface after being -26~
i~356~9 used to lubricate a ~irst bearing or bearing surface; and that oil 102 to be received by any ~earing or bearing surface is relatively cool and filtered~
The lower frame assembly, the upper frame assembly~
S input drive, accumulator and other components and mec'nan-isms required to render the cone crusher operative are constructed, arranged, and operated in the manner similar to comparable assembly, mechanisms and components described in U.S. Patent 4,168,036.
It is understood that although I have shown the pre-ferred embodiments of my invention that various modifica-tions ma~ be made in details thereof without departing from the spirit as comprehended by the following claims.
~ , .
Claims (57)
1. A cone crusher; comprising:
(a) frame means;
(b) center shaft housing means carried by said frame means;
(c) bore means formed in a central portion of said center shaft housing means;
(d) center shaft means, disposed in said bore means of said center shaft housing means, movable in an axial direction with respect to said center shaft housing means but rotation-ally stationary with respect to said center shaft housing means;
(e) piston means coacting with said center shaft means for moving said center shaft means in said axial direction;
(f) eccentric means rotatably disposed about said center shaft housing means;
(g) drive means connected to said eccentric means to drive same in a predetermined driven direc-tion;
(h) crusher head means carried by said center shaft housing means and having skirt means disposed for coaction with said eccentric means such that when said eccentric means is driven by said drive means said crusher head means is gyrated and rotated with respect to said eccentric means;
(i) plain bearing means disposed between coacting surfaces of said eccentric means and said skirt means; and (j) roller bearing means disposed between coacting surfaces of said eccentric means and said center shaft housing means.
(a) frame means;
(b) center shaft housing means carried by said frame means;
(c) bore means formed in a central portion of said center shaft housing means;
(d) center shaft means, disposed in said bore means of said center shaft housing means, movable in an axial direction with respect to said center shaft housing means but rotation-ally stationary with respect to said center shaft housing means;
(e) piston means coacting with said center shaft means for moving said center shaft means in said axial direction;
(f) eccentric means rotatably disposed about said center shaft housing means;
(g) drive means connected to said eccentric means to drive same in a predetermined driven direc-tion;
(h) crusher head means carried by said center shaft housing means and having skirt means disposed for coaction with said eccentric means such that when said eccentric means is driven by said drive means said crusher head means is gyrated and rotated with respect to said eccentric means;
(i) plain bearing means disposed between coacting surfaces of said eccentric means and said skirt means; and (j) roller bearing means disposed between coacting surfaces of said eccentric means and said center shaft housing means.
2. The cone crusher of claim 1: wherein said plain bearing means is formed on an outside surface of said eccentric means.
3. The cone crusher of claim 2: wherein said plain bearing means is formed from babbit metal.
4. The cone crusher of claim 2: wherein said plain bearing means extends from a first location proximate a first extremity of said eccentric means to a second location spaced a predetermined distance from a second extremity of said eccentric means.
5. The cone crusher of claim 4: wherein said crusher head means and said skirt means are disposed for axial movement with respect to said eccentric means; and said predetermined distance is such, that for the maximum axial movement of said skirt means with respect to said eccentric means in a direction moving a first extremity of said skirt means away from said second extremity of said eccentric means, that said second location of said plain bearing means will still be between said eccentric means and said skirt means.
6. The cone crusher of claim 2: wherein said plain bearing means includes an oil location on said outside surface of said eccentric means and oil passage means are provided for conducting lubricating oil to said oil location.
7. The cone crusher of claim 6: wherein said oil location is located a predetermined arcuate distance from an imaginary radial line intersecting the point of maximum eccentricity of said outside surface of said eccentric means and the center of rotation of said eccentric means.
8. The cone crusher of claim 7: wherein said predeter-mined arcuate distance of said oil location precedes said immaginary radial line in the predetermined driven direction of rotation of said eccentric means.
9. The cone crusher of claim 8: wherein said predeter-mined arcuate distance of said oil location lies between 135 radial degrees and 165 radial degrees from said imaginary radial line.
10. The cone crusher of claim 6: wherein said oil location is sized about said outside surface of said eccentric to span approximately twenty degrees in arcuate distance.
11. The cone crusher of claim 10: wherein said oil location extends axially along said outside surface of said eccentric means to terminate proximate the axial extremities of said plain bearing means.
12. The cone crusher of claim 6: wherein said oil passage means is arcuately centered with respect to said oil location.
13. The cone crusher of claim 12: wherein said oil passage means includes a radial channel extending through said eccentric means from said oil location on said outside surface of said eccentric means to oil groove means on said inside surface of said eccentric means, and further includes first oil passage means extending into said center shaft housing means connecting with second oil passage means extending through said center shaft housing means to oil entry means.
14. The cone crusher of claim 13: wherein said plain bearing means is spaced from said skirt means and said oil location is sized to extend into said outside surface of said eccentric means so that as said eccentric means is driven in said predetermined driven direction and coacts with said skirt means oil collected at said oil location is wiped over said plain bearing means and the coacting surface of said skirt means.
15. The cone crusher of claim 14: wherein said coaction between said eccentric means and said skirt means forces oil to pass over said plain bearing means and said skirt means in directions towards said first and said second extremities of said eccentric means.
16. The cone crusher of claim 15: wherein oil passes from between said eccentric means and said skirt means without being directed to any other bearing means, and conduit means are provided to return the oil to an oil reservoir without the oil being directed to any other bearing.
17. The cone crusher of claim 16: wherein third oil passage means are provided extending through said skirt means for directing the oil, passing from between said eccentric means and said skirt means at said first extremity, to said oil reservoir.
18. The cone crusher of claim 1: wherein said roller bearing means includes a first roller bearing assembly located proximate a first extremity of said eccentric means and a second roller bearing assembly located proximate a second extremity of said eccentric means.
19. The cone crusher of claim 18: wherein said first roller bearing assembly and said second roller bearing assembly both completely encircle said center shaft housing means and are encircled by said eccentric means.
20. The cone crusher of claim 19: wherein said oil groove means are formed in said inside surface of said eccentric means to communicate with fourth oil passage means formed in said center shaft housing means to receive lubricating oil therefrom and to direct the lubricating oil directly to said roller bearing means and without first directing the oil to any other bearing means.
21. The cone crusher of claim 20. wherein said oil groove means also communicates with space means, provided between said inner surface of said eccentric means and an outer surface of said center shaft housing means, sized just sufficiently to permit lubricating oil to flow directly from said oil groove means to said first roller bearing assembly and directly from said oil groove means to said second roller bearing assembly.
22. The cone crusher of claim 21: wherein oil from said first roller bearing assembly flows into lubrication channel means provided through said skirt means and then to said oil reservior and oil from said second roller bearing assembly flows into said oil reservoir.
23. The cone crusher of claim 1; wherein:
(a) thrust bearing means are disposed between said crusher head means and said center shaft means to facilitate mounting of said crusher head means and relative movement between said crusher head means and said center shaft means;
(b) said thrust bearing means including ball sector means having oil groove means formed in a predetermined surface thereof;
(c) said thrust bearing means further including socket means having a relatively smooth surface disposed for coaction with said predetermined surface of said ball sector means; and (d) said oil groove means being spaced one from the other a predetermined distance so that every point on said surface of said socket means will be exposed to said oil groove means for each cycle of the cone crusher.
(a) thrust bearing means are disposed between said crusher head means and said center shaft means to facilitate mounting of said crusher head means and relative movement between said crusher head means and said center shaft means;
(b) said thrust bearing means including ball sector means having oil groove means formed in a predetermined surface thereof;
(c) said thrust bearing means further including socket means having a relatively smooth surface disposed for coaction with said predetermined surface of said ball sector means; and (d) said oil groove means being spaced one from the other a predetermined distance so that every point on said surface of said socket means will be exposed to said oil groove means for each cycle of the cone crusher.
24. The cone crusher of claim 23: wherein said oil groove means includes a plurality of circular oil grooves and a plurality of radial oil grooves intersecting said circular oil grooves; said predetermined distance between said oil grooves being determined according to the equation:
D = 2 (R) (tan. ? a) where D is the distance point on said ball sector means travels upon the surface of said socket means for each cycle of gyration of the cone crusher;
R is the length of the radius line from an imaginary point P determined by the intersection of an axis of rotation x of an outer surface of said eccentric means;
<a is the angle at which said axis X and said axis Y
meet.
D = 2 (R) (tan. ? a) where D is the distance point on said ball sector means travels upon the surface of said socket means for each cycle of gyration of the cone crusher;
R is the length of the radius line from an imaginary point P determined by the intersection of an axis of rotation x of an outer surface of said eccentric means;
<a is the angle at which said axis X and said axis Y
meet.
25. The cone crusher of claim 23: wherein oil channel means are formed in said center shaft means communicating at one end with said oil groove means and at another end with oil passage means formed in said center shaft housing means.
26. The cone crusher of claim 25: wherein said oil passage means in said center shaft housing means includes oil passageway means extending from an oil entry opening in said center shaft housing means to an oil exit opening located in an inner surface of said center shaft housing means which defines said bore means; and sleeve means located in said bore means and including an elongated slot extending through said sleeve means and interconnecting said exit opening from said center shaft housing means to said oil passage means in said center shaft.
27. The cone crusher of claim 26: wherein said elongated slot is sized and positions so that said exit opening and said oil passage means are in communication, one with the other, for all axial positions of said center shaft.
28. The cone crusher of claim 1; wherein:
(a) said eccentric means includes flywheel means rotatable with said eccentric means, (b) counterweight means carried by said flywheel means so as to be spaced from, and concentric with, said eccentric means;
(c) said counterweight means being sized and positioned to extend from a location proximate said first extremity of said eccentric means to a location proximate said second extremity of said eccentric means.
(a) said eccentric means includes flywheel means rotatable with said eccentric means, (b) counterweight means carried by said flywheel means so as to be spaced from, and concentric with, said eccentric means;
(c) said counterweight means being sized and positioned to extend from a location proximate said first extremity of said eccentric means to a location proximate said second extremity of said eccentric means.
29. The cone crusher of claim 28: wherein said flywheel means includes circular wall means surrounding and spaced from said outer surface of said eccentric means; and said counterweight means is formed by securing a counterweight wall, between said circular wall means and said outer sur-face of said eccentric means for a predetermined circular distance, to define a counterweight pocket open along a plane intersecting said counterweight wall and said circular wall means; and filling said counterweight pocket with relatively dense material to form a counterweight.
30. The cone crusher of claim 29: wherein said relatively dense material is lead.
31. The cone crusher of claim 29: wherein said counter-weight wall includes a substantially circular portion substantially concentric with said circular wall, and end portions connecting said circular portion to said circular wall.
32. The cone crusher of claim 31: wherein said counter-weight wall diverges upwardly and outwardly, from at least a portion of said circular wall at a predetermined angle.
33. The cone crusher of claim 32: wherein said predetermined angle is such as to induce the flow of oil downwardly and away from said counterweight means during rotation thereof with said eccentric means.
34. The cone crusher of claim 33: wherein additional portions of said circular wall means are formed at said pre-determined angle.
35. In a cone crusher having a stationary housing and a driven eccentric, rotatably disposed about the stationary housing and, disposed for coaction with a crusher head so that when said eccentric is driven said crusher head gyrates and rotates about said eccentric: a bearing arrangement therefore; comprising:
(a) plain bearing means disposed between said eccentric and said crusher head to facilitate movement of one with respect to the other; and (b) roller bearing means disposed between said eccentric and said stationary housing to facilitate rotation of said eccentric thereabout.
(a) plain bearing means disposed between said eccentric and said crusher head to facilitate movement of one with respect to the other; and (b) roller bearing means disposed between said eccentric and said stationary housing to facilitate rotation of said eccentric thereabout.
36. The bearing arrangement of claim 35: wherein said plain bearing means facilitates axial as well as rotative movement of said crusher head with respect to said eccentric.
37. The bearing arrangement of claim 36: wherein said plain bearing means is formed on an outside surface of said eccentric.
38. The bearing arramgement of claim 37: wherein said plain bearing means is formed from babbit metal.
39. The bearing arrangement of claim 37: wherein said plain bearing means extends from a first location proximate a first extremity of said eccentric to a second location spaced a predetermined distance from a second extremity of said eccentric.
40. The bearing arrangement of claim 39: wherein said crusher head includes a skirt and both said crusher head and skirt are disposed for axial movement with respect to said eccentric; and said predetermined distance is such, that for the maximum axial movement of said skirt with respect to said eccentric in a direction moving a first extremity of said skirt away from said second extremity of said eccentric, that said second location of said plain bearing means will still be between said eccentric and said skirt.
41. The bearing-arrangement of claim 37: wherein said plain bearing means includes an oil location on an outside surface of said eccentric; and oil passage means are provided for conducting lubricating oil to said oil location.
42. The bearing arrangement of claim 41: wherein said oil location is located a predetermined arcuate distance from an imaginary radial line intersecting the point of maximum eccentricity of said outside surface of said eccentric and the center of rotation of said eccentric.
43. The bearing arrangement of claim 42: wherein said predetermined arcuate distance of said oil location precedes said imaginary radial line in the predetermined direction of rotation of said eccentric.
44. The bearing arrangement of claim 43: wherein said predetermined arcuate distance of said oil location lies between 135 radial degrees and 165 radial degrees from said imaginary radial line.
45. The bearing arrangement of claim 41: wherein said oil location is sized about said outside surface of said eccentric to span approximately twenty degrees in arcuate distance.
46. The bearing arrangement of claim 45: wherein said oil location extends axially along said outside surface of said eccentric to terminate proximate the axial extremities of said plain bearing means.
47. The bearing arrangement of claim 41: wherein said oil passage means is arcuately centered with respect to said oil collecting location.
48. The bearing arrangement of claim 47: wherein said oil passage means includes a radial channel extending through said eccentric from said oil location on said outside surface of said eccentric to oil groove means on an inside surface of said eccentric, and further includes first oil passage means extending into said housing connecting with second oil passage means extending through said housing to an oil entry means.
49. The bearing arrangement of claim 48: wherein said plain bearing means is spaced from said skirt, and said oil location is sized to extend into said outside surface of said eccentric so that as said eccentric rotates in a predetermined direction and coacts with said skirt means, oil collected at said oil location is wiped over said plain bearing means and the coacting surface of said skirt means.
50. The bearing arrangement of claim 49: wherein said coaction between said eccentric and said skirt means forces oil to pass over said plain bearing means and said skirt means in directions towards said first and said second extremities of said eccentric.
51. The bearing arrangement of claim 50: wherein oil passes from between said eccentric and said skirt means without the being directed to any other bearing means, and conduit means are provided to return the oil to an oil reservoir without the oil being directed to any other bearing.
52. The bearing arrangement of claim 51: wherein third oil passage means are provided extending through said skirt means for directing the oil, passing from between said eccentric and said skirt means at said first extremity, to said oil reservoir.
53. The bearing arrangement of claim 35: wherein said roller bearing means includes a first roller bearing assembly located proximate a first extremity of said eccen-tric and a second roller bearing assembly located proximate a second extremity of said eccentric.
54. The bearing arrangement of claim 53: wherein said first roller bearing assembly and said second roller bearing assembly completely encircle the stationary housing.
55. The bearing arrangement of claim 54: wherein said oil groove means are formed in said inside surface of said eccentric to communicate with oil passage means formed in said stationary housing to receive lubricating oil therefrom and to direct the lubricating oil directly to said roller bearing means and without first directing the oil to any other bearing means.
56. The bearing arrangement of claim 55: wherein said oil groove means also communicates with space means, pro-vided between said inner surface of said eccentric and an outer surface of said stationary housing, sized just sufficiently to permit lubricating oil to flow directly from said oil groove means to said first roller bearing assembly and directly from said oil groove means to said second roller bearing assembly.
57. The bearing arrangement of Claim 56: wherein oil from said first roller bearing assembly flows into lubrication channel means provided through said skirt means and then to said oil; and oil from said second roller bearing assembly flows into said oil reservoir.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US40187982A | 1982-07-26 | 1982-07-26 | |
| US401,879 | 1982-07-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1235679A true CA1235679A (en) | 1988-04-26 |
Family
ID=23589614
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000433110A Expired CA1235679A (en) | 1982-07-26 | 1983-07-25 | Cone crusher |
Country Status (6)
| Country | Link |
|---|---|
| AU (1) | AU1697983A (en) |
| CA (1) | CA1235679A (en) |
| DE (1) | DE3326626A1 (en) |
| FR (4) | FR2530495B1 (en) |
| IT (1) | IT1207467B (en) |
| NZ (1) | NZ205012A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2505265A1 (en) | 2011-03-29 | 2012-10-03 | Sandvik Intellectual Property AB | Cone crusher, bearing plate, and kit of bearing plates |
| US10352363B2 (en) | 2013-09-19 | 2019-07-16 | Sandvik Intellectual Property Ab | Cone crusher, bearing plate, and kit of bearing plates |
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|---|---|---|---|---|
| TW265277B (en) * | 1993-02-15 | 1995-12-11 | Clyde Ind Ltd Trading As Jaques | |
| AU665900B2 (en) * | 1993-02-15 | 1996-01-18 | Clyde Industries Limited Trading As Jacques | Crusher apparatus |
| GB0225332D0 (en) * | 2002-10-31 | 2002-12-11 | Jarvis Tim | Cone crusher |
| US7566018B1 (en) * | 2008-11-04 | 2009-07-28 | Fl Smidth A/S | Rock crusher counterweight oil deflection plates |
| US8444075B2 (en) | 2009-09-15 | 2013-05-21 | Metso Minerals Industries, Inc. | Concentrated bi-density eccentric counterweight for cone-type rock crusher |
| EP2696980B1 (en) | 2011-04-13 | 2015-06-03 | Metso Minerals, Inc. | Cone crusher and processing plant for mineral material |
| TWI480101B (en) * | 2012-05-04 | 2015-04-11 | Fan Kung Chi | Movable cone support device and inverted cone cone crusher |
| CN103212460B (en) * | 2013-03-18 | 2015-07-08 | 浙江武精机器制造有限公司 | Gyratory crusher |
| CN103521291B (en) * | 2013-08-28 | 2017-01-25 | 浙江双金机械集团股份有限公司 | Main shaft copper sleeve specially used for cone sand making machine and lubricating and cooling method |
| CN104588153A (en) * | 2015-01-28 | 2015-05-06 | 浙江浙矿重工股份有限公司 | Multiple-cylinder cone crusher drive unit |
| RU2583676C1 (en) * | 2015-03-16 | 2016-05-10 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Кубанский государственный технологический университет" (ФГБОУ ВПО "КубГТУ") | Disintegrator |
| FR3041026B1 (en) | 2015-09-15 | 2017-10-20 | Ifp Energies Now | METHOD FOR CHARACTERIZING THE NETWORK OF FRACTURES OF A FRACTURE SLOT AND METHOD FOR OPERATING IT |
| CN111561517A (en) * | 2020-04-30 | 2020-08-21 | 广东省创力智能机械设备有限公司 | Mining machinery supporting assembly and manufacturing process thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1600780A (en) * | 1924-05-17 | 1926-09-21 | Symons Brothers Company | Gyratory crusher |
| US1945791A (en) * | 1928-09-17 | 1934-02-06 | Smith Engineering Works | Intercone mill |
| US1894601A (en) * | 1929-02-20 | 1933-01-17 | Nordberg Manufacturing Co | Crushing machine |
| US2310737A (en) * | 1940-07-26 | 1943-02-09 | Nordberg Manufacturing Co | Shaftless cone crusher and tilting member therefor |
| US2359987A (en) * | 1941-02-14 | 1944-10-10 | Nordberg Manufacturing Co | Pedestal type crusher |
| US2670142A (en) * | 1947-08-04 | 1954-02-23 | Nordberg Manufacturing Co | Attrition mill |
| DE1027042B (en) * | 1952-04-10 | 1958-03-27 | Axel Wuertzen Kjellgaard | Cone crusher |
| US2713461A (en) * | 1952-04-10 | 1955-07-19 | Axel W Kjelgaard | Gyratory crusher |
| FR1066891A (en) * | 1952-07-29 | 1954-06-10 | Gen Pour Les Travaux De Genie | Advanced crusher |
| US2814450A (en) * | 1953-10-29 | 1957-11-26 | Nordberg Manufacturing Co | Lubrication means for gyratory crushers and feed mechanism therefor |
| US3417932A (en) * | 1966-03-28 | 1968-12-24 | Allis Chalmers Mfg Co | Gyratory crusher |
| DE1507568A1 (en) * | 1966-05-20 | 1969-07-17 | Kloeckner Humboldt Deutz Ag | Rotary crusher with hydraulically supported crushing cone |
| US3384312A (en) * | 1966-07-25 | 1968-05-21 | Allis Chalmers Mfg Co | Spiderless gyratory crusher having frictionless bearings |
| US3396916A (en) * | 1966-10-28 | 1968-08-13 | Allis Chalmers Mfg Co | Fluid pressure operated adjustment and release for gyratory crushers and the like |
| FR1529735A (en) * | 1967-04-25 | 1968-06-21 | Neyrpic Ets | Lubrication provision applicable to gyratory crushers |
| DE2000141A1 (en) * | 1970-01-02 | 1971-07-15 | Kloeckner Humboldt Deutz Ag | Lubricant supply for gyratory crusher |
| US4034922A (en) * | 1976-06-08 | 1977-07-12 | Allis-Chalmers Corporation | Gyratory crusher with bushing assembly between inner eccentric antifriction bearing |
| US4206881A (en) * | 1978-02-22 | 1980-06-10 | Litton Systems, Inc. | Cone crusher anti-spin mechanism |
| US4192472A (en) * | 1978-04-17 | 1980-03-11 | Johnson Louis W | Cone crusher |
-
1983
- 1983-07-19 AU AU16979/83A patent/AU1697983A/en not_active Abandoned
- 1983-07-23 DE DE19833326626 patent/DE3326626A1/en not_active Withdrawn
- 1983-07-25 NZ NZ205012A patent/NZ205012A/en unknown
- 1983-07-25 CA CA000433110A patent/CA1235679A/en not_active Expired
- 1983-07-26 FR FR8312356A patent/FR2530495B1/en not_active Expired
- 1983-07-26 IT IT8322233A patent/IT1207467B/en active
- 1983-07-26 FR FR8312354A patent/FR2530493B1/en not_active Expired
- 1983-07-26 FR FR8312353A patent/FR2530492B1/en not_active Expired
- 1983-07-26 FR FR8312355A patent/FR2530494B1/en not_active Expired
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2505265A1 (en) | 2011-03-29 | 2012-10-03 | Sandvik Intellectual Property AB | Cone crusher, bearing plate, and kit of bearing plates |
| WO2012130515A1 (en) | 2011-03-29 | 2012-10-04 | Sandvik Intellectual Property Ab | Cone crusher, bearing plate, and kit of bearing plates |
| CN103534032A (en) * | 2011-03-29 | 2014-01-22 | 山特维克知识产权股份有限公司 | Cone crusher, bearing plate, and kit of bearing plates |
| US9388855B2 (en) | 2011-03-29 | 2016-07-12 | Sandvik Intellectual Property Ab | Cone crusher, bearing plate, and kit of bearing plates |
| US10352363B2 (en) | 2013-09-19 | 2019-07-16 | Sandvik Intellectual Property Ab | Cone crusher, bearing plate, and kit of bearing plates |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2530492B1 (en) | 1988-05-27 |
| FR2530495A1 (en) | 1984-01-27 |
| FR2530494B1 (en) | 1987-02-27 |
| FR2530495B1 (en) | 1987-02-27 |
| IT8322233A0 (en) | 1983-07-26 |
| DE3326626A1 (en) | 1984-01-26 |
| FR2530494A1 (en) | 1984-01-27 |
| FR2530493B1 (en) | 1987-02-27 |
| FR2530493A1 (en) | 1984-01-27 |
| AU1697983A (en) | 1984-02-02 |
| NZ205012A (en) | 1989-01-06 |
| FR2530492A1 (en) | 1984-01-27 |
| IT1207467B (en) | 1989-05-25 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |