CA1084886A - Gyratory crusher having an eccentric shaft supported by pairs of spaced bearing assesmblies - Google Patents

Abstract

GYRATORY CRUSHER HAVING AN ECCENTRIC SHAFT SUPPORTED BY
PAIRS OF SPACED BEARING ASSEMBLIES

Abstract A gyratory type crusher having a stationary frame and a generally conical crushing head rotatably mounted on an eccentric shaft so that the crushing head is gyrated upon rotation of the eccentric shaft.
The stationary frame includes a concave which surrounds the crushing head and cooperates with it to form an annular crushing chamber. The eccentric shaft is rotatably supported at its lower end by a pair of vertically spaced radial roller bearings which are in turn axially slideably received in a cen-tral bore in the frame. The conical crushing head is rotatably supported on the upper end of the eccentric shaft by a pair of vertically spaced radial roller bearing assemblies which are axially slideably received within a bore in the conical head and which are received around the upper end of the shaft.
The spaced bearing assemblies function to compensate for overturning moments applied to the crushing head to provide greater bearing wear and are axially slideably removable to facilitate replacement.

Description

10~4~6 Background of the Invention The invention pertains to crushers for reducing rock and ore aggregate to the desired sizes. More particularly, the invention pertains to a gyratory or cone type crusher in which a crushing head is supported by and rotatably mounted on an upright eccentric shaft so that the crushing head is gyrated upon rotation of the eccentric shaft. Examples of such prior art gyratory crushers are shown in United States Patent No. 3,743,193, issued July 3, 1973 to DeDiemar et al. and United States Patent No. 2,634,061, issued April 7, 1953 to Rumpel. The stationary frame of such crushers have a crushing bowl including a concave which surrounds the crushing head and which cooperates therewith to form an annular crushing chamber. The material to be crushed such as rock and ore is distributed to the crushing chamber by feeding the material into a hopper above the cone and concave, which material then falls into the crushing chamber. The eccentric shaft is continually rotated to cause the head to gyrate within the concave effecting a crushing -action upon the material.
Summary of the Invention The present invention provides a gyratory crusher having a stationary frame and a concave mounted in said frame, said frame including a vertically extending first bore, an eccentric shaft including an eccentric upper end and a lower end, at least one anti-friction bearing assembly received in said first bore, said at least one bearing assembly supporting said shaft lower end for rotation relative to said frame, a crushing head rotatably mounted on said upper end of said eccentric shaft for gyratory movement there- -by and relative to said concave to effect a crushing action with said concave, said crushing head including a downwardly facing uniform diameter bore there-in for receiving said eccentric upper end of said shaft, and a pair of vertically spaced apart anti-friction cyllndrical and radial thrust type bearing assemblies slideably received upwardly in an axial direction in said downwardly facing bore and located around said upper end of said eccentric shaft, a removable spacer slideably received in said downwardly facing bore and located between said bearing assemblies, said assemblies being of equal

-2-1~89~16 diameter whereby said pair of bearing assemblies can be removed and replaced and rotationally support said crushing head on said upper end of said eccentric shaft, said frame also having a generally horizontal, annular sur-face, an anti-friction thrust bearing assembly mounted on said annular sur-face, said head mounted on said thrust bearing assembly for rotation relative to said annular surface and whereby vertical thrust is absorbed by said thrust bearing assembly.
The invention also provides a gyratory type crusher having a stationary frame and a concave mounted in said frame, said frame including a ~:~
vertically extending first bore, an eccentric shaft including an eccentric upper end and a lower end, a first pair of vertically spaced anti-friction bearing assemblies slideably received in an axial direction in said first bore and can be axially slid outwardly from said bore so as to facilitate removal and replacement of said assemblies, said bearing assemblies support-ing said shaft lower end for rotation relative to said frame, a crushing head rotatably mounted on said upper end of said eccentric shaft for gyratory movement thereby and relative to said concave to effect a crushing action with said concave, said crushing head including a downwardly facing second -bore of uniform diameter therein for receiving said eccentric upper end of said shaft, and a second pair of vertically spaced anti-friction cylindrical and radial thrust type bearing assemblies slideably received upwardly in an axial direction in said second bore and being of equal diameter for removal from and replacement therein, a removable spacer slideably received in said downwardly facing bore and located between said bearing assemblies, said .
second pair of assemblies rotationally supporting said crushing head on said upper end of said eccentric shaft, said frame also having a generally horizontal, annular surface, an anti-friction thrust bearing assembly mounted on said annular surface, said head mounted on said thrust bearing assembly for rotation relative to said annular surface and whereby vertical thrust is absorbed by said thrust bearing assembly.

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~084~86 The spaced bearing assemblies have been found to provide substan-tial advantages over the use of the single large bearing assemblies shown for example, in the DeDiemar patent cited above. For example, the spaced -2b-~1 1'D~4886 apart bearing assemblies provide more stable support for the conical crush-ing head because there is less likelihood of the rollers becoming skewed or misaligned within the bearing cages. Furthermore, vibration or skidding of the rollers is substantially reduced thereby increasing the bearing life. Using a pair of relatively small bearings rather than a single bearing, has the further advantage that the smaller bearings are more easily handled during assembly or replacement. The bearings used in a gyratory crusher are often large enough that it is necessary to use mechanical means such as a crane or the like to support the bearings during assembly or replacement. The smaller 10. bearings, however, can be handled manually and do not necessitate the use of such a crane. Furthermore, wear on bearings used in a gyratory crusher is often localized to either one or the other ends of the bearing due to overbearing moments applied to the conical crushing head. Use of two relatively small spaced bearings rather than a single bearing can compensate for such localized wear and can substantially reduce the cost of bearing replacement since it is often practical to replace only one of the worn bearings.
The gyratory crusher of the present invention includes a further substantial advantage over the other prior art crushers in that each of the bear-ing assemblies used in the gyratory crusher of the invention can be axially 20. slideably removed with a minimum of effort and at a minimum cost.
Brief Description of the Drawings FIGURE 1 is a vertical cross-sectional view through a gyratory crusher embodying the present invention.
FIGURE 2 is an enlarged view of the vertically spaced bearing assemblies shown in FIG, 1.

1. 1 , 1084~86 Description of the Preferred Embodiment As shown in FIG. 1, the gyratory crusher provided by the pre-sent invention includes a main frame F which is rigidly and stationarily mount-ed to any suitable supporting structure (not shown). The main frame F has an annular concave supporting ring 2 supported on an annular upwardly diverging surface 3 of the frame wall 1~ The ring 2 is resiliently held against the sur-face 3 by means of a series of tension bolts 4 and compression springs 5, which springs act against the flange 6 of the main frame F and against a spring re-taining ring 7 located on the lower end of the bolts 4. Thus the springs 5 per-10. mit the upper ring 2 to move upwardly when excessive loads are encountered by the crushing members which wlll be described. The structure referred to above is further described in U. S, Patent No, 3, 744, 728, issued July 10, I973 to Treppish and assigned to the same assignee as this appLication.
The upper ring 2 supports a support bowl 8 to which is fixed a manganese steel concave 9. The concave 9 and a conical crushing head 10 function to define therebetween an annular crushing chamber 11. Material to be crushed is fed into a hopper 12, which is supported by the upper ring 2, and then falls into the annular crushing chamber 11 wherein relative gyratory movement between the conical crushing head 10 and the concave 9 acts to 20. crush the material against the concave 9 in a known manner, The conical crushing head 10 is supported for gyratory motion on an eccentric shaft 13. The lower end of the eccentric shaft 13 is rotatably mounted within a central vertically extending bore 14 in the main frame F.
The lower end of the shaft 13 is supported by a pair of separate vertically 1084~86 :

spaced apart radial roller bearing assemblies 16 and 17, each of which isaxially slideably received in the bore 14. As best shown in FIG. 2J the outer race 18 of the lower roller bearing assembly 16 is supported by a shoulder 19 of the bore 14, and the inner race 23 of the bearing assembly 16 is supported by a collar l9a secured to the eccentric shaft 13 by a set screw l9b. The upper bearing assembly 17 is maintained in vertically spaced relation from the lower bearing assembly 16 by a pair of concentric annular spacing rings 21 and 22. One of the rings 21 is slideably received in the bore 14 and is posi-tioned between the outer races 18 of the bearings and the other annular ring 22 10 is slideably received around the lower end of the shaft 13 and is positioned between the inner races 23 of the bear ings 16 and 17. The eecentric shaft 13 includes a shoulder 24 supported by the bearing assembly 17.
The eccentric shaft 13 also includes a radially outwardly extending flange 26 intermediate its length which is supported at its periphery by a horizontally disposed bearing assembly 27. The bearing assembly 27 is sup-ported on annular surface 25 of the main frame F and in turn provides support for the lower surface of the eccentric shaft flange 26. The two vertically spaced radial roller bearing assemblies 16 and 17 and the bearing assembly 27 thus rotatably support the eccentric shaft 13 for rotation with respect to the main 20 frame F. In order to provide for such rotation of the shaft 13, a large bevel gear 29 is secured to the lower end of shaft 13. The bevel gear 29 meshes with a bevel pinion 31 in turn fixed to a drive shaft 32. Power is furnished to the drive shaft by a multiple-V pulley 33 which is in turn driven by a conventional power source (not shown).

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1~)84886 ~
The conical crushing head 10 is rotatabLy supported on the eccentric upper end of the eccentric shaft 13 by a generally horizontally disposed bearingassembly 28 and by a pair of separated vertically spaced radial roller bearing assemblies 34 and 36. The generally horizontally disposed bearing assembly 28 is supported by the upper periphery of the radially extending flange 26 and in turn supports a lower annular surface 37 of the crushing head lO. The gen-eral purpose of the bearing assembly 28 is to accommodate vertical load placed onthecrushing head 10. The conical crushing head 10 includes a central axially extending bore 38 for slideably receiving the spaced bearing assemblies 34 and 10 36 therein. The upper bearing assembly 36 is received against a cover plate - 39 and a shoulder 41. The bearing assemblies 34 and 36 are held in spaced relation by a pair of concentric annular spacing rings 42 and 43. The bore 38 also includes a pair of annular grooves 44 and 46 around each of the bearing assemblies 34 and 36, respectively, and connected to fluid passages 47 and 48.
Due to the loads applied to the bearing assemblies used in gyra-tory crushers such as that of the present invention, the bearing assemblies are subjected to wear and must be replaced on occasion. The gyratory crusher of the invention provides substantial improvements over the prior art crushers by including means to facilitate removal and replacement of such worn bear-20 ing assemblies. As previously stated, the bearing assemblies 16 and 17 areaxially slideably received in the bore 14, and the bearing assemblies 34 and 36 are axially slideably received in a similar bore 38. To replace the bearing assemblies 34 and 36, the concave supporting ring 2 can be removed from the frame F, and the conical crushing head 10 along with the outer races 34a and 36aof the bearing assemblies 34 and 36 can then be pulled upwardly off the eccentric shaft 13. By injecting fluid under pressure through the passages 47 and 48, the outer races 34a and 36a of the bearing assemblies can then be slideably removed 1~)84~3~6 from the bore 38 if push rods are extended through bores 45 and used to push the bearing assemblies out of the bore 38. In order to replace the bearing assemblies 16 and 17, the eccentric shaft 13 and the inner bearing races 23 are pulled upwardly out of the frame F. Then the outer bearing races 18 of the bearing àssemblies 16 and 17 can be axially slideably removed from the bore 14.
In order to further facilitate replacement of the bearing assemblies, each of the bearing assemblies 16, 17, 34 and 36 is the same size and interchangeable.
During the operation of the gyratory crusher, it is desirable that the crushing action be relatively evenly distributed in the crushing chamber 11, however, it has been found that the crushing action may occur only in the por-tion lla of the annular chamber 11, i. e., that area between the concave 9 and the extreme outer peripheral edge of the conical crushing head, When the crushing action is thus restricted, the forces on the lower peripheral edge of the conical crushing head cause an overturning moment to be applied to the crushing head 10. The spaced bearing assemblies of the present invention sup-porting the eccentric shaft and the conical crushing head have substantial ad-vantages in compensating for such an overturning moment. The use of two spaced bearing assemblies 34 and 36 rather than a single large bearing assem-bly substantially reduces the possibility of skewing or misalignment of the bearing rollers within the respective bearing cages and also reduces ~ribration and skidding of the rollers in the bearing thereby increasing the bearing life and providing a more stable support between the conical crushing head and the upper end of the eccentric shaft. Furthermore, wear on a single large bearing used in a gyratory crusher is often localized to either one or the other of the ends of the bearing, particularly in cases where the crushing head is subjected ... .. . . . .. ..

~8~ 6 to an overturning moment as previously described, The use of two spaced bearings rather than a single bearing can substantially reduce the cost of bearing replacement since it is often practical to replace only one of the worn bearings. Furthermore, use of a pair of relatively small bearings rather than a single large bearing facilitates much easier handling of the bearings during assembly or replacement.
Resume The bearing assembly used in the gyratory crusher of the pre-sent invention thus has a plurality of advantages over the prior art. Since 10. pairs of spaced bearing assemblies are used rather than single large bearings, the bearing assemblies wear longer and provide a more stable support for the conical crushing head and the eccentric shaft because the rollers used in smaller bearing assemblies are less apt to skew, become misaligned, skid or vibrate.
Furthermore, the pairs of spaced bearing assemblies are less subject to un-even bearing wear. ~Iowever,i in the event that there is localized wear, the smaller bearings can be replaced at less cost. An additional advantage of the present invention is that the bearing assemblies are axially slideably positioned in their respective bores in such a manner that they can be relatively easily removed and replaced, 20.

Claims (2)

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

1. A gyratory crusher having a stationary frame and a concave mounted in said frame, said frame including a vertically extending first bore, an eccentric shaft including an eccentric upper end and a lower end, at least one anti-friction bearing assembly received in said first bore, said at least one bearing assembly supporting said shaft lower end for rotation relative to said frame, a crushing head rotatably mounted on said upper end of said eccentric shaft for gyratory movement thereby and relative to said concave to effect a crushing action with said concave, said crushing head including a downwardly facing uniform diameter bore therein for receiving said eccen-tric upper end of said shaft, and a pair of vertically spaced apart anti-friction cylindrical and radial thrust type bearing assemblies slideably received upwardly in an axial direction in said downwardly facing bore and located around said upper end of said eccentric shaft, a removable spacer slideably received in said downwardly facing bore and located between said bearing assemblies, said assemblies being of equal diameter whereby said pair of bearing assemblies can be axially slideable downwardly out of and removed from said bore for replacement, said assemblies-rotationally support-ing said crushing head on said upper end of said eccentric shaft, said frame also having a generally horizontal, annular surface, an anti-friction thrust bearing assembly mounted on said annular surface, said head mounted on said thrust bearing assembly for rotation relative to said annular surface and whereby vertical thrust is absorbed by said thrust bearing assembly.

2. A gyratory type crusher having a stationary frame and a concave mounted in said frame, said frame including a vertically extending first bore, an eccentric shaft including an eccentric upper end and a lower end, a first pair of vertically spaced anti-friction bearing assemblies slideably received in an axial direction in said first bore and can be axially slid outwardly from said bore so as to facilitate removal and replacement of said assemblies, said bearing assemblies supporting said shaft lower end for rotation relative to said frame, a crushing head rotatably mounted on said upper end of said eccentric shaft for gyratory movement thereby and relative to said concave to effect a crushing action with said concave, said crushing head including a downwardly facing second bore of uniform diameter therein for receiving said eccentric upper end of said shaft, and a second pair of vertically spaced anti-friction cylindrical and radial thrust type bearing assemblies slideably received upwardly in an axial direction in said second bore and being of equal diameter for removal from and replacement therein, a removable spacer slideably received in said downwardly facing bore and located between said bearing assemblies, said second pair of assemblies rotationally supporting said crushing head on said upper end of said eccentric shaft, said frame also having a generally horizontal, annular surface, an anti-friction thrust bearing assembly mounted on said annular surface, said head mounted on said thrust bearing assembly for rotation relative to said annular surface and whereby vertical thrust is absorbed by said thrust bearing assembly.