US3151816A - Crusher apparatus and method of manufacture - Google Patents

Description

Oct. 6, 1964 A. B. HANSE ETAL 3,151,816

CRUSHER APPARATUS AND METHOD OF MANUFACTURE Filed June 18, 1962 3 Sheets-Sheer l Oct. 1964 A. B. HANSE ETAL 3,151,816

CRUSHER APPARATUS AND METHOD OF MANUFACTURE Filed June 18, 1962 3 Sheets-Shae? 2 INVENTORB- aw 29258 1964 A. B. HANSE ETAL 3,

CRUSHER APPARATUS AND METHOD OF MANUFACTURE Filed June 18, 1962 3 Sheets-Shes: 5

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yam/2 fia M gm L27 IQMZMZM Z United States Patent M 3,151,316 CRUSfi-IER APPARATU AND PVIETEUD 0T0 MANUFACNJAE Albert E. Ianse and Leonard N. Kint, Cedar Rapids, Iowa, assignors to Pettihone Ivinlliken Corporation, a corporation of Delaware Filed June 18, 1962, Ser. No. 203,5)65 7 Claims. (Cl. 241-191) The present invention pertains to an apparatus for crushing rock or the like, and, more particularly, relates to an impeller structure and the method of manufacturing the same.

While features of the present invention might be used in the manufacture of various types of rock crushers and other apparatus employing a rotor of similar characteristics, the invention was devised primarily for use in connection with a rock crusher of the type wherein an impeller or rotor is rotated about a generally horizontal axis. The rock to be crushed is deposited on the rotor where it is impacted against hammers on the rotor and thrown against a screen grate for further impacting and classification. In devices of this type, the rotor and hammers are severely abused by the conditions under which the apparatus is operated. The rotor must be large and sturdy to withstand the centrifugal forces, to hold the hammers in place and to not be rendered unserviceable because of the constant impacting and battering occasioned by contact between the moving rotor and hammers and the stone to be crushed. in addition, it is desirable to have a rotor with as high a moment of inertia as possible to simplify the motive power requirements, and stresses thereon.

Necessarily, the hammers are subjected to damage and wear and must be made so that they can be replaced periodically as this takes place. The rotor must be constructed so that replacement of the hammers is easily performed and that the hammers are securely held in place during operation. The conditions under which operation occurs will tend to loosen and/ or damage many conventional types of fastening devices. Means are provided to permit ready determination of when the hammer wear is such that the hammers should be replaced.

We have devised a novel rotor structure and method of manufacturing the same which is ideally suited to operate under the adverse conditions found in a rock crusher of this type. The rotor readily may be fabricated from the plurality of pieces. It incorporates a hammer mounting structure which will securely hold the hammers in place and not tend to loosen in use. Yet, despite the adverse conditions, the removal and replacement of the hammers is extremely simple and is not impaired by the use of the machine. The rotor has a high moment of inertia. A comparatively inexpensive, self-aligning, hearing is incorporated for the rotor.

The hammer mounting structure is such that it does not seriously weaken the rotor such as occurs in many prior art devices by reason of the existence of deep pockets or the like provided to incorporate the hammer mounting structure. Using the present invention, it is possible to produce a rotor having as many as four hammers which will withstand the punishing service of rotors of this type. Using prior art practices, many have con- 3,15 1,8 16 Patented Oct. 6, 1964 sidered that the rotors were unduly weak when they incorporated even only three hammers.

With many prior art hammer mountings, it was necessary that the machine be stopped after some period of use and the hammer mountings retightened. The hammer mounting of our structure is such that no retightening is necessary. The operation of the machine, the various forces and blows on the hammers, etc., will not loosen the hammers. As will be apparent from the following description, the hammers are securely seated against a rearward face (with respect to the direction of movement) so that they will not move, bend or break. Furthermore, the support of this face extends relatively high on the hammer. This, plus the manner in which the hammer is wedged and locked in place, contributes to the elimination of the necessity for retightening the hammers after they have had some use.

Further objects and advantages will become apparent from the following description taken in conjunction with the drawings in which:

FIGURE 1 is a perspective view of a rock crusher with portions of the enclosure removed;

FIGURE 2 is a side view of a portion of the crusher of FIG. 1;

FIGURE 3 is a View of the rotor with a portion broken away to illustrate its fabrication; and

PiGURE 4 is a partial section as viewed at line 4-4 of PEG. 1.

Although the following disclosure offered for public dissemination is detailed to ensure adequacy and aid understanding, this is not intended to prejudice that purpose of a patent which is to cover each new inventive concept therein no matter how others may later disguise it by variations in form or additions or further improvements. The claims at the end hereof are intended as the chief aid toward this purpose; as it is these that meet the requirement of pointing out the parts, improvements, or combinations in which the inventive concepts are found.

The crusher comprises an enclosure or frame generally 1%. As viewed in FIGURE 1, the front and top of the enclosure have been removed to better illustrate the structure of the crusher. There are two side walls 11 and a back, not shown. An impeller or rotor generally 12 is mounted between side walls 11. At each end of the rotor are shafts 13 suitably journaled in bearings 14. A power means, not shown, is connected to a shaft 13 to rotate the rotor in a direction such that the top of the rotor, as viewed in FIGURE 1, is moving away from the viewer.

We have devised a method of mounting bearings 14 to inexpensively achieve self alignment Without the usual expense of self aligning bearings. Bearing 14 is secured to a mounting member 16, which at two sides contacts wear plates 17. At the other two sides, spring bars 18 are secured to mounting member 16 by brackets 1%. It will be observed that brackets 19 space the ends of bars 18 away from the sides of mounting member 16. Bolts 2%) are threaded into frame 10 and fixed in place by jam nuts 21. The inner ends of bolts 20 bear against the central portion of spring bars 18, urging those bars toward mounting member 16. Thus, spring bars 18 urge mounting member 16 toward the Wear plates 17. At the same time, the resiliency of the spring bars permit abutment 28 that forms a shoulder 31.

mounting member 16 to float with respect to frame 10. To facilitate this, preferably the edges of mounting member 16 in contact with the wear plates 17, are slightly curved as viewed in cross section (not shown).

An outside flinger 22 is secured to each of shafts 13 immediately beyond the outer face of bearings 14. On the side adjacent impeller 12, mounting member 16 abuts frame of the machine. A lock bolt 23 secured to frame 14) extends into a pocket 24 in mounting member 16. Pocket 24 is larger than the bolt and thus does not inhibit the mounting member from floating with respect to the frame. At the same time, it prevents substantial movement of the mounting member and bearing.

Four hammers 27 :are mounted on the periphery of rotor 12. Each of hammers 27 is positioned in a pocket. At one side, each pocket is defined by an abutment 28. Abutment 28 faces forwardly with respect to direction of rotation 29. There is an undercut 3h inwardly of Hammer 27 has a projection 32 that enters undercut 3i and locks under shoulder 31. The bottom 33 of hammer 27 is spaced above the base 34 of the pocket in which the hammer is received. A portion of base 34 forms a camming surface 35 which is positioned at an obtuse angle with respect to the face of abutment 23. Hammer 27 has a pressure face 37. A wedge 38 has a pressure face 39 which contacts pressure face 37 of hammer 27. Wedge 38 also has a camming surface 44 in contact with camming surface 35 of the rotor body. While wedges 38 could be made in a single piece, preferably they are in a plurality of parts as illustrated in FIGURE 1.

A plurality of wedging screws 42 are threaded into wedges 38. Each wedging screw has a head 43 which bears against a presssure plate 44 mounted as an insert on the forwardly wall of the pocket. One of the advantages of our invention, as will be apparent from the description herein, is that the rotor body may be formed of mild steel. more easily worked or machined than are some other materials. However, to prevent damage to the mild steel body of the rotor, pressure plates 44 are welded therein to bear against the heads 43 of the wedging screws. Wedges 38 have abutments 45 on each end thereof. At the center, each hammer has recesses defining a web 46. A centering member 47 is notched to fit about web 46. Centering member 47 is secured to the body of the rotor by a cap screw 48.

Doors 51 form a part of the enclosure 10 and are positioned at each end of rotor 12; The doors are hinged to the remainder of the enclosure and are provided with latches, not shown, which engage hooks 52 to hold the door in a closed position. The bottom 53 of the door openings are at a level corresponding to the distance of the top of unworn hammers 27 from the axis of shaft 13. Thus, as hammers 27 wear, the extent of the wear may be determined by positioning the hammers as illustrated in FIGURE 2. The difference in elevation between the top of the hammers 27 and the plane defined by the bottoms 53 of the door openings will exhibit the extent to which the hammers 27 have been worn.

The bottoms 53 of the door openings are cut out to receive an insert 54. Insert 54 forms a part of enclosure 10 and normally is held in place by the tongue and groove edges thereof. After door 51 has been opened, insert 54 may be lifted out of its position. It thereby provides an opening to enable hammers 27 to be moved longitudinally out of and into the enclosure 10 and the pockets on the rotor.

To remove and replace hammers 27, the hammer to be removed and replaced first is positioned as illustrated in FIGURE 2. Doors 51 are opened to obtain access to the interior of the crusher. Inserts 54 are lifted out of place after the opening of doors 51. Wedging screws 42 are turned in a direction such that they are threaded farther into wedges 38, thus providing additional space This is relatively inexpensive and it is between pressure plates 44 and the pressure face 37 of the hammers. Cap screw 48 is removed along with centering member 47. Upon completion of these operations, the hammer 27 may be moved longitudinally through one of the openings provided by the removal of an insert 54. Thereafter, a new hammer is similarly slid into place from one end of the rotor, pressure screws 42 are extended from each of wedges 38 and the wedges pushed up so that the contact of faces 37 and 39 firmly seats projection 32 under shoulder 31 of abutment 28. After all of the wedges 33 have been securely pressed against hammer 27, centering member 47 may be replaced in the position illustrated in FIGURE 4. Each successive hammer 27, is replaced in a similar manner.

The relative positioning of the rearward abutment 28, (and its shoulder), pressure faces 37 and 39, camming surfaces 35 and 4d, and pressure screws 42 is important. It is this that enables the hammers to be readily changed, yet prevents them from loosening in service. Those familiar with the art will appreciate that the structure is such that the hammer pockets are relatively shallow as compared to many such devices. Thus, the rotor is not particularly weakened and the moment of inertia of the rotor reduced.

In operation the rock to be crushed is deposited onto rotor 12. The movement of the rotor and its hammers will throw the rock in the general direction of a screen grate 55. Grate 55 comprises a plurality of spaced bars 56. The rock will be fractured by the initial impact between the rock and the hammers, by the impact against the screen grate, or both.

FIGURE 3 illustrates the structure making up the body of rotor 12. It is formed of a plurality of mild steel plates. In the illustrated embodiment, there are two end plates 57, two outer intermediate plates 58, two inner intermediate plates 59 and a center plate 60. End plates 57 and center plate 60 have axial openings 61, corresponding in size to the diameter of shaft 13. One or more of these plates 57 and 69 are provided with keyway 62 to enable the rotor body to be rotatively secured to shaft 13. The two inner intermediate plates 59 have axial openings 63 larger than axial openings 61. The outer intermediate plates 58 have axial openings 64 larger than the axial openings 63. The corners of the plates are beveled to form welding scarfs. Preferably, these scarfs extend about the entire periphery of the rotor body except for the portion defining the bottom of the hammer pockets, i.e., bottom surfaces 34 and 35. In the usual instance, plates 57-60 will be formed to shape prior to assembly, except for the surfaces that are to be relatively smooth and planar. In this respect, the two important surfaces are those that define abutment 28 and camming surface 35. These will have a slight amount of excess metal left thereon, so that after the rotor body is formed, they may be machined to a relatively exact configuration.

To assemble the rotor body, all of the plates except for the end plates 57, are assembled and welded. This.

may be done in sequence or all may be assembled before welding. In any event, the two inner intermediate plates 59 are Welded to the center plate 60. The two outer welds 66 are made in the scarfs provided therefor. Annular inner welds 67 are made in the V groove, or fillet space, provided by the adjacent surfaces of plates 59 and 60. Similarly, outer intermediate plates 58 are welded to inner intermediate plates 59 by outer welds 68 and inner welds 69. After the last intermediate plate on each end, e.g. plate 58, has been welded on the inside, e.g. weld 69, the end plate 57 on that end can be fastened in place. This is done solely by an outside weld 70.

Since shaft 13 is supported in bearings 14 immediately beyond each end of the rotor body, the end portions of the body are not as severely stressed as are the more central portions thereof. Thus, outside welds are sufficient to connect plates 57-58. In the portions of the body that will be more severely stressed, additional inner welds 67 and 69 are supplied. Those familiar with the welding art will be readily cognizant of the fact that inner welds 67 and 69 are relatively easy to form. A V groove is provided by the abutting parts to serve as a fillet space. The increased size of the central opening coupled with the angular position of the V groove makes it relatively easy for a welder to produce a good weld. Were the V groove in the form of a scarf such as that provided for the outer welds 66, 68 and 70, a welder would have extreme difficulty in doing the job even if the axial opening were large enough to permit the insertion of the welding apparatus and to permit visual inspection of the welding operation. Other than the attachment of end plates 57, the sequence in which the welds are made is of no particular significanoe. No inference with respect to sequence is to be derived from the order of recitation of steps in the attached claims, other than that named therein as being in a specific sequence.

While the term rock has been used herein, this is for the purpose of illustration only and is employed to comprehend the type of materials that generally are processed in a machine of this type. Other materials that fall within this category would be slag, etc.

We claim:

1. A rotor for an apparatus for crushing rock or the like and adapted to be mounted on a shaft for rotation in a given direction, said rotor having a central opening to receive said shaft and comprising a plurality of parts having abutting faces normal to said shaft, said parts being welded together both inside and outside, said central opening on the outside parts being shaped to fit to the shaft, said rotor having a pocket extending parallel to the shaft opening and defined by a bottom wall and a forwardly and a rearwardly wall as related to said direction of ro tation, said rearwardly wall having a rearwardly extending undercut in the portion thereof spaced inwardly from the periphery of the rotor and defining a shoulder, a hammer in said pocket with one side abutting the rearwardly wall and hooked under the shoulder with the inner portion of the hammer being spaced from the bottom wall, the opposite side of the hammer having a pressure face extending inwardly and toward said one side, a wedge spaced from the forwardly wall and having a pressure face contacting said pressure face of the hammer and a second face against a portion of said bottom wall, said second face and said pressure face being positioned such that the included angle between them is an acute angle, means releasably bearing between the rotor at the forwardly wall and the wedge to drive and releasably hold the wedge against the hammer, whereby upon releasing said wedge it may be moved toward the forwardly Wall and away from the hammer to permit the hammer to be removed.

2. A rotor as set forth in claim 1, wherein the distance from the axis of the shaft opening to the periphery of the rotor at said forwardly wall is substantially less than the distance to the periphery at said rearwardly wall, and said hammer projects beyond the periphery of the rotor.

3. In a rock crushing apparatus having a casing and a rotor adapted to be mounted on a shaft for rotation about an axis in a given direction, said rotor having a central opening to receive said shaft, the improvement comprising: said rotor including a plurality of parts having abutting faces normal to said shaft, said parts being welded together both inside and outside, said central opening in the outside parts being shaped to fit to the shaft, said rotor having an external pocket extending parallel to the shaft opening and defined by a bottom wall and a forwardly and rearwardly wall as related to said direction of rotation, said rearwardly wall having a rearwardly extending undercut in the portion thereof spaced inwardly from the periphery of the rotor and defining a shoulder, a hammer in said pocket with one side abutting the rearwardly wall and hooked under the shoulder with the inner portion of the hammer being spaced from the bottom wall, the opposite side of the hammer having a pressure face extending inwardly and toward said one side, a wedge spaced from the forwardly wall and having a pressure face contacting said pressure face of the hammer and a second face against a portion of said bottom wall, said second face and said pressure face being positioned such that the included angle between them is an acute angle, means releasably bearing between the rotor at the forwardly wall and the wedge to releasably hold the wedge against the hammer, whereby upon releasing said wedge it may be moved toward the forwardly wall and away from the hammer to permit the hammer to be removed; and access door means in the sides of the casing intersected by said axis, one portion of the door opening being closer to said axis than is said bottom wall whereby the hammer may be moved endwise therethrough, a second portion of the door opening being the same distance from the axis as is the outer portion of an unworn hammer to provide a gauge to determine the amount of hammer wear.

4. In a rotor for an apparatus for crushing rock wherein the rotor is adapted to be mounted on a shaft for rotation about an axis in a given direction, said rotor having a central opening to receive said shaft, the improvement comprising: a pocket extending parallel to the shaft opening and defined by a bottom wall and a forwardly and a rearwardly wall as related to said direction of rotation, said rearwardly wall having a rearwardly extending undercut in the portion thereof spaced inwardly from the periphery of the rotor and defining a shoulder, a hammer in said pocket, with one side abutting the rearwardly wall and hooked under the shoulder with the inner portion of the hammer being spaced from the bottom wall, the opposite side of the hammer having a pressure face extending inwardly and toward said one side, a wedge spaced from the forwardly wall and having a pressure face contacting said pressure face of the hammer and a second face against a portion of said bottom wall, said second face and said pressure face being positioned such that the included angle between them is an acute angle, means releasably bearing between the rotor at the forwardly wall and the wedge to releasably hold the Wedge against the hammer, whereby upon releasing said wedge it may be moved toward the forwardly wall and away from the harnmer to permit the hammer to be removed.

5. A rotor improvement according to claim 4 in which the rotor and hammer at its rearward face are provided with interfitting means for ensuring retension of the hammer in centered position while held by the wedge.

6. A rotor improvement according to claim 4 in which the means releasably bearing between the rotor and the wedge includes a screw means for driving the wedge and hammer in place.

7. In a rotor for an apparatus for crushing rock wherein the rotor is adapted to be mounted on a shaft for rotation about an axis in a given direction, said rotor having a central opening to receive said shaft, the improvement comprising: a pocket extending parallel to the shaft opening and defined by a bottom wall and a forwardly and a rearwardly wall as related to said direction of rotation, said rearwardly wall having an outer portion and a rearwardly extending undercut in the portion thereof spaced inwardly from the periphery of the rotary and defining a shoulder at the inner end of the outer portion, the outer portion of the rearwardly Wall being slanted forwardly from a radial line to the Wall at the shoulder, the portion of the bottom wall adjacent the forwardly Wall being at an obtuse angle to said outer portion of the rearwardly Wall, a hammer in said pocket with one side abutting the rear wardly wall and hooked under the shoulder with the inner portion of the hammer being spaced from the bottom wall, the opposite side of the hammer having a pressure face extending inwardly and toward said one side, said pressure face and said outer portion being positioned with the included angle therebetween being an acute angle, a wedge spaced from the forwardly wall and having a pressure face contacting said pressure face of the hammer and a second face against said portion of the bottom wall, and a plurality of screws threaded into the wedge along lines generally normal to said outer portion, said screws abutting the forwardly wall to hold the wedge and hammer in place, whereby screwing said screws further into said wedge will release the screws from the forwardly wall and provide space for moving the wedge away from the hammer so that it may be removed.

References Cited in the file of this patent UNITED STATES PATENTS Kempshall Sept. 30, 1913 Bock Dec. 1, 1931 Hanse May 29, 1956 Rollins Dec. 2, 1958

Claims (1)

1. 4. IN A ROTOR FOR AN APPARATUS FOR CRUSHING ROCK WHEREIN THE ROTOR IS ADAPTED TO BE MOUNTED ON A SHAFT FOR ROTATION ABOUT AN AXIS IN A GIVEN DIRECTION, SAID ROTOR HAVING A CENTRAL OPENING TO RECEIVE SAID SHAFT, THE IMPROVEMENT COMPRISING: A POCKET EXTENDING PARALLEL TO THE SHAFT OPENING AND DEFINED BY A BOTTOM WALL AND A FORWARDLY AND A REARWARDLY WALL AS RELATED TO SAID DIRECTION OF ROTATION, SAID REARWARDLY WALL HAVING A REARWARDLY EXTENDING UNDERCUT IN THE PORTION THEREOF SPACED INWARDLY FROM THE PERIPHERY OF THE ROTOR AND DEFINING A SHOULDER, A HAMMER IN SAID POCKET, WITH ONE SIDE ABUTTING THE REARWARDLY WALL AND HOOKED UNDER THE SHOULDER WITH THE INNER PORTION OF THE HAMMER BEING SPACED FROM THE BOTTOM WALL, THE OPPOSITE SIDE OF THE HAMMER HAVING A PRESSURE FACE EXTENDING INWARDLY AND TOWARD SAID ONE SIDE, A WEDGE SPACED FROM THE FORWARDLY WALL AND HAVING A PRESSURE FACE CONTACTING SAID PRESSURE FACE OF THE HAMMER AND A SECOND FACE AGAINST A PORTION OF SAID BOTTOM WALL, SAID SECOND FACE AND SAID PRESSURE FACE BEING POSITIONED SUCH THAT THE INCLUDED ANGLE BETWEEN THEM IS AN ACUTE ANGLE, MEANS RELEASABLY BEARING BETWEEN THE ROTOR AT THE FORWARDLY WALL AND THE WEDGE TO RELEASABLY HOLD THE WEDGE AGAINST THE HAMMER, WHEREBY UPON RELEASING SAID WEDGE IT MAY BE MOVED TOWARD THE FORWARDLY WALL AND AWAY FROM THE HAMMER TO PERMIT THE HAMMER TO BE REMOVED.

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