US3508716A

US3508716A - Rock crusher

Info

Publication number: US3508716A
Authority: US
Inventors: James G Daly
Original assignee: Westinghouse Air Brake Co
Current assignee: Westinghouse Air Brake Co
Priority date: 1968-05-01
Filing date: 1968-05-01
Publication date: 1970-04-28
Anticipated expiration: 1987-04-28

Description

J. G DALY ROCK CRUSHER April 28, 1-970 2 Sheets-Sheet 1 Original Filed Feb. 25. 1966 Z INVENTOR. 14/1455 6 .044)

April 28, 1970 J. G. DALY 3,503,716

ROCK CRUSHER Original Filed Feb. 25. 1966 2 Sheets-Sheet 2 INVENTOR. JAM5 DAMY F 5 BY United States Patent 3,508,716 ROCK CRUSHER James G. Daly, Chicago, Ill., assignor to Westinghouse Air Brake Company, Pittsburgh, Pa., a corporation of Pennsylvania Continuation of application Ser. No. 530,035, Feb. 25, 1966. This application May 1, 1968, Ser. No. 725,850 Int. Cl. B02c 4/12 US. Cl. 241--204 Claims ABSTRACT OF THE DISCLOSURE Horizontal gyratory type of rock crusher in which the periphery of a crusher roll, freely journalled on an eccentric, which drives the roll with a back and forth gyratory action, cooperates with crusher jaws on opposite sides of the roll to define crushing zones for crushing rock to a selected size. The crusher jaw spaced from the downrunning side of the drive eccentric is concave, having a crushing face defining a crushing zone converging toward the crusher roll as the jaw extends in a downward direction. The crusher jaw spaced from the uprunning side of the drive eccentric is non-concave, having a fiat or convex crushing face converging toward and diverging from the crusher roll as it extends vertically past a line of closest proximity to the crusher roll.

BACKGROUND OF THE INVENTION This application is a continuation of application Ser. No. 530,035, filed Feb. 25, 1966, now abandoned.

This invention relates to improvements in crushers for rock and the like and more particularly relates to an improved form of rock crusher of the gyratory roll type.

Heretofore, rock crushers in the form of a vertical axis gyratory roll have been commonly used for crushing rock and the like. Similar horizontal axis gyratory roll crushers, in which a gyratory crusher roll is moved back and forth by an eccentric rotating about a horizontal axis, and cooperating with opposed crusher jaws on opposite sides of the axis of rotation of the eccentric have also been made and used, particularly because the horizontal axis roll crusher, in many cases, can do the work of a primary and secondary crusher or secondary and a tertiary crusher and the cooperation of the gyratory crusher roll with the opposed crushing jaws gives two crushing zones with a much higher capacity than prior designs of vertical axis gyratory roll crushers having a single crushing zone.

Gyratory roll crushers of the generally horizontal type with two diametrically opposed crushing zones, however, have never come into wide commercial use principally because of choking problems between the crusher roll and the jaw on the upcoming side of the eccentric rotatably driving the crusher roll. This choking becomes so serious as to frequently stall the crusher, causing undue wear, frequent damage and burying of the crusher, where choking is not seen in time to stop operation of the feeder conveyor for the crusher.

SUMMARY AND OBJECTS OF THE INVENTION A principal object of the present invention is to cure the deficiencies heretofore present in gyratory roll crushers by providing a novel and improved crusher having the advantage of two opposed crushing zones and so constructed and arranged as to avoid the choking problems heretofore present in such crushers.

A further object of the invention is to provide an improved form of horizontal axis gyratory roll crusher having diametrically opposed crushing zones in which choking of the crusher is avoided by arranging the crushice ing zone on the upcoming side of the drive member for the roll, to diverge from the crusher roll beneath the axis of rotation of the roll.

Still another and more detailed object of the invention is to provide a horizontal axis gyratory roll crusher having diametrically opposed crusher jaws in which the crusher jaw 0n the downrunning side of the eccentric drive means is concave toward the roll shell and converges toward the roll shell in a downward direction, and in which the opposite crusher jaw is non-concave (specifically having a shape which is between the limits of fiat and convex-toward-the-roll-shell) and converges toward and diverges from the roll shell as the jaw extends vertically past a line of closest proximity to the roll shell.

These and other objects of the invention will appear from time to time as the following specification proceeds and with reference to the accompanying drawings wherein:

FIGURE 1 is a top plan view of a horizontal axis gyratory roll crusher constructed in accordance with the principles of the present invention;

FIGURE 2 is a transverse sectional view taken through the crusher, substantially along line IIII of FIGURE 1;

FIGURE 3 is a longitudinal sectional view taken substantially along line IIIIII of FIGURE 1;

FIGURE 4 is a transverse sectional view taken substantially along line IVIV of FIGURE 3; and

FIGURE 5 is a diagrammatic view illustrating the principles of the present invention.

DESCRIPTION OF PREFERRED EMBODIMENT OF INVENTION In the embodiment of the invention illustrated in the drawings, I have shown a gyratory crusher comprising a frame or housing 11 having parallel spaced

side walls

12, 12 extending upwardly from a base 13 having an open portion 14 for the discharge of aggregate therethrough. The

side walls

12, 12 are suitably tied together as by tie bars 15 at opposite ends of said side walls. Vertical abutment walls 16 extend between the side walls 12 adjacent opposite ends thereof and are braced by parallel horizontally extending bracing plates 17, extending between the side walls 12 and abutting the outer sides of the abutment walls 16.

The

walls

12, 12 form supports for aligned bearing boxes 19 for antifriction bearings 20, shown as being oppositely disposed roller end thrust bearings and forming bearing supports for a drive shaft 21. The drive shaft 21 has an eccentric midportion 22 forming a mounting for a crusher roll 23, shown in the drawings as being in the general form of a roll shell. Bearing caps 24, bolted or otherwise secured to the side walls 12, are provided to retain the bearing boxes 19 and bearings 20 in position. A flywheel 25 is shown in FIGURE 2 as being keyed or otherwise secured to the shaft 21 and serves as a counterweight for said shaft. A drive pulley (not shown) or other conventional drive means may be secured to the opposite end of said shaft. The roll shell 23 is rotatably mounted on the eccentric central portion 22 of the shaft 21 on antifriction bearings 27, herein shown as being opposed end thrust types of roller bearings. As shown in FIGURE 2, the bearings 27 form a bearing support on the eccentric 22 for a sleeve 29 having an end flange 30 extending radially of one end thereof and having a tapered outer face 31 inclined inwardly from the outer to the inner end of said end flange and engaging a corresponding tapered inner peripheral face 32 of the roll shell 23.

An annular take-up wedge 33 is slidably mounted on the opposite end portion of the sleeve 29 from the flange 30 and has a tapered peripheral or wedging surface 35 inclined inwardly from the outer to the inner side thereof and engaging a corresponding inner peripheral tapered surface 36 of the roll shell 23. A series of tie bolts 37 having lock nuts 39 threaded on opposite ends thereof are provided to take up on the take-up wedge 33 and rigidly retain the roll shell 23 to the sleeve 29, to rotate therewith about the antifriction bearings 27.

Rotation of the shaft 21 will rotate the roll shell 23 therewith under no load conditions and will also move the roll shell back and forth toward and from oppositely disposed crusher jaws 40 and 41 mounted in s-wingable

jaw bracket arms

43, 43. Under load conditions, however, the roll shell will tend to creep in a direction opposite to the direction of rotation of its drive eccentric. The

jaw bracket arms

43, 43 are of a similar construction and support the respective jaws 40 and 41 in a similar manner, so the same reference characters will be applied to each bracket arm, and one only need herein be shown or described in detail.

The

bracket arms

43, 43 are mounted on

transverse shifts

44, 44 mounted at their opposite ends in the

side walls

12, 12 adjacent the upper end portions thereof in suitable bearings (not shown), closed by

end caps

45, 45. As shown in FIGURES 3 and 4, the jaw bracket arms 43 include transverse plates 46 welded or otherwise secured to the shafts 44 and depending therefrom.

Each plate 46 is shown as being rein-forced by parallel spaced vertically extending ribs 47 extending upwardly about the shaft 44 and spaced apart along said shaft, and welded or otherwise secured thereto. The ribs 47 in turn are retained in spaced relation with respect to each other by generally horizontally extending spacer plates 49, spaced between said ribs, intermediate the ends thereof. The ribs 47 have a semi-cylindrical socket member 48 extending thereacross having an outwardly opening semi-cylindrical socket 50 formed therein. The socket 50 is engaged by a rounded end 51 of a toggle link 52. The opposite end of the toggle link 52 has a rounded end 53 engaging a semi-cylindrical socket 55 formed in an abutment member 56 resting on the top surface of a horizontal plate 57 and abutting the inner wall of the vertical plate 16 and retained to the

plates

57 and 16 by a retainer plate 58. Shims 59 are interposed between the inner face of the plate 16 and the socket member 56, to adjust the spacing between the crushing face of an associated crusher jaw and the periphery of the roll shell 23. The toggle links 52 are shown in FIGURE 4 as extending for substantially the width of the plate 46 and as being of a relatively thin cross-section to break upon excessive loads on the crusher jaws 40 and 41, and thereby act as safety links which may readily be replaceable.

The rounded ends 51 and 53 of each toggle link 52 are retained to their sockets by a compression spring 60 encircling a tension rod 61 and seated between the rear face of the abutment plate 16 and a washer retained to said tension link by an adjustment nut 62. The tension link 61 has a clevis 63 on its inner end extending between spaced bosses 64 extending inwardly of a pair of central ribs 47, beneath the socket member 48, and pivotally connected to said ribs and bosses, as by a pivot pin 65.

Each jaw bracket arm 43 has a flange 66 extending inwardly of the lower end of the plate 46 having a gib 67 extending upwardly therefrom. The gib 67 has an inclined upper face conforming to the angle of inclination to an inclined lower face 69 of an associated crusher jaw. The inclined upper face of the gib 67 terminates into a face 70 perpendicular to the inner wall of the plate 46 and fitting the lower end portion of the asso ciated crusher jaw.

The upper end of the jaw 40 has a tapered wedging face 71 inclined oppositely from the face 69 and engaged by a tapered wedging face 73 of a wedge 74. The wedge 74 extends across the ribs 47 and engages wedging faces 75 of inwardly projecting portions of the ribs 47 beneath 4 the shaft 44. The wedge 74 is drawn toward the plate 46, to wedge the crusher jaw into tight engagement with the inner face of the plate 46 by nuts and bolts 76, extending through said wedge and plate, and tightened from the outer side of said plate.

It is apparent from the foregoing that the bracket arms 43 are each of a similar construction. The portions of the crusher jaws 40 and 41 clamped or wedged to said bracket arms by the wedges 74 are also of a similar construction. The jaws 40 and 41 may thus be interchanged upon reversal in the direction of rotation of the shaft 21 to render the jaw crusher reversely operable.

The

ribs

47, 47 have the horizontal legs of angle plates 77 extending across the top surfaces thereof and secured thereto. The vertical legs of said angle plates are positioned to extend downwardly along the inner sides of the

ribs

47, 47 to positions adjacent the

wedges

74, 74 to close the space from the top of the crusher to the crusher jaws 40 and 41 and form in effect the end walls of a hopper 78. Side plates 79 extend between the vertical legs of the

angle plates

77, 77 on each side of the crusher and cooperate with the vertical legs of the

angle plates

77, 77 to form the side walls of said hopper.

Plates

80, 80 extend downwardly of the

side plates

79, 79 along opposite ends of the roll shell 23 and terminate into arcuate faces 81 extending radially inwardly of the periphery of the roll shell 23 and cooperate with the periphery of said roll shell and the crusher jaws 40 and 41 to retain rock to said crusher jaws to be crushed by gyratory motion of the crusher roll 23.

Referring now in particular to the crusher jaws 40 and 41, the crusher jaw 40 is shown as having a convex crusher face 83 while the crusher jaw 41 is shown as having a concave crusher face 85.

The concave face 85 of the crusher jaw 41 may be a. conventional form of crusher jaw face and cooperates with the periphery of the roll shell 23 to form a passageway converging toward the roll shell as the crusher jaw extends downwardly. With the periphery of the roll shell it defines a first crushing zone, converging toward the roll shell in a downward direction.

Where, according to the past practice described above, the two crusher jaws have concave faces like the concave face 85 of the jaw 41, the material between the jaw and the roll shell on the uprunning side of the eccentric 22 tends to choke and even to stall, as previously mentioned, with the resultant burying of the crusher. The roll shell 23, however, freely cooperates with the concave crusher face 85 of the jaw 41 on the downrunning side of the eccentric without any choking.

It has been found that where the concavity of the crusher face of the crusher jaw on the uprunning side of the eccentric is removed, forming a crusher zone or passageway between the roll shell and jaw which converges in a downward direction toward a line (AA in FIGURE 5) of closest proximity and then diverges in a further downward direction from that line, this choking is entirely eliminated.

The jaw 40 on the uprunning side can be made nonconcave by making it flat as indicated at 83a in FIGURE 5 at which configuration the benefits of the present in vention begin to appear and choking is no longer a problem. By extending the principles of this invention further, and making the uprunning face convex (within the limits of an allowable angle of nip), as indicated at 83 in the drawings, the maximum benefits of the invention will be realized by eliminating choking entirely and enabling the crusher to operate dependably and consistently at its maximum operating capacity.

Referring now to FIGURE 5 for a summary of the present invention, the jaw face 85 on the downrunning side is concave and the jaw face on the uprunning side is in a range of non-concave shapes between the limits of the flat surface 83a and a convex surface 83, with the benefits of the present invention increasing generally as the convexity is increased up to the maximum angle of nip which is well recognized in the art and depends on the size and surface conditions of the jaw and roll and on the material being crushed.

Also as shown in FIGURE 5, the crushing zone on the uprunning side along jaw 40 converges in a downward direction toward a line L of closest proximity between the jaw and roll, and then the crushing zone diverges in a further downward direction. One preferred arrangement, shown in FIGURE 5, places the line L in a horizontal plane AA including the rotational axis of the drive shaft 21.

While I have herein shown and described one form in which the invention may be embodied, it may readily be understood that various variations and modifications in the invention may be attained without departing from the spirit and scope of the novel concepts thereof.

I claim as my invention:

1. In a crusher for rock and the like,

a housing,

a horizontal roll shell within said housing and extending transversely thereof,

eccentric drive means for said roll shell extending along the axis of said roll shell and adapted to be rotatably driven about a horizontal axis, crusher jaws disposed on opposite sides of said roll shell and cooperating therewith to provide generally vertically extending crusher zones on the uprunning and downrunning sides of said eccentric drive means,

the crusher jaw on the uprunning side of said eccentric drive means having a non-concave shape between the limits of flat and convex-toward-the-roll-shell and converging toward and diverging from the roll shell as the jaw extends vertically past a line of closest proximity to the roll shell, and

the crusher jaw on the downrunnning side of the eccentric drive means converging toward the roll shell in a downward direction.

2. The structure of claim 1,

wherein the crusher jaw on the uprunning side of the eccentric drive means is convex toward the roll shell.

3. The structure of claim 1,

wherein the crusher jaw on the uprunning side of the eccentric drive means is flat,

4. The structure of claim 1,

wherein the crusher jaw on the downrunning side of the eccentric drive means is concave toward the roll shell.

5. The structure of claim 1,

wherein said line of closest proximity of the crusher jaw to the roll shell on the uprunning side of the eccentric drive means is substantially in a horizontal plane intersecting the rotational axis of the eccentric drive means.

6. The structure of claim 5,

wherein the crusher jaw on the downrunning side of the eccentric drive means converges toward the roll shell in a downward direction below said horizontal plane.

7. The structure of claim 1,

wherein bracket arms are transversely pivoted to the housing above the roll shell and on opposite sides of the roll shell and form clamping supports for the crusher jaws, wherein toggle links abut the opposite sides of said bracket arms from said crusher jaws and space said crusher jaws with respect to the periphery of said roll shell, wherein spring means maintain said bracket arms in engagement with said toggle links and accommodate release of said jaws against said toggle links, and wherein said bracket arms interchangeably clamp said crusher jaws and maintain said crusher jaws in spaced relation with respect to the face of said roll shell and thereby accommodate interchanging of said crusher jaws from one side of said roll shell to the other and reversal of rotation of said eccentric drive means and roll shell. 8. The structure of claim 7, wherein the crusher jaw spaced from the roll shell on the uprunning side of the eccentric drive means has a crushing face which is convex toward the roll shell and the crusher jaw spaced from the roll shell on the downrunning side of the eccentric drive means has a crushing face which is concave toward the roll shell. 9. The structure of claim 1, wherein the eccentric drive means comprises a shaft extending through said roll shell and rotatably journalled in said housing adjacent its opposite ends and having an eccentric midportion, wherein said roll shell is freely journalled on said eccentric midportion of said shaft, and wherein the crusher jaw spaced from said roll shell on the downrunning side of said eccentric midportion has a crushing face which is concave toward the roll shell. 10. The structure of claim 9, wherein the crusher jaw on the uprunning side of said eccentric drive means has a crushing face convex toward the roll shell and diverging from the roll shell as it extends beneath a substantially horizontal plane extending through the axis of rotation of said eccentric drive means, and wherein said crusher jaws are interchangeably mounted to accommodate operation of the crusher upon reverse rotation of said roll shell.

References Cited UNITED STATES PATENTS 2,582,734 1/1952 Adams 24l239 FOREIGN PATENTS 472,240 2/ 1929 Germany.

JAMES M. MEISTER, Primary Examiner US. Cl. X.R. 83-285