US1247701A - Ore-pulverizer. - Google Patents

Description

C. O. MICHAELSEN.

OBE PULVERIZER.

APPLlcATIoM ElLED QCT. 24, 1914.

Lwymc. rammed Nov. 27, 191?.

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V mmm C. 0. MICHAELSEN.

ORE PULVERIZER.

APPLICATION FILED 001.24. 1914.

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C. 0. MICHAELSEN.

ORE PULVERIZER.

APPLICATION EILED ocT. 24. 1914.

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ORE PULVERIZER.

APPLICATION FILED ocr. 24, 1914.

LMYL Mmm Nov. 27, 19m

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lggfwi @MM rari @K0 CHARLES 0. `llvCHGI-IAEI..SEN', 0F OMAHA, NEBRASKA, ASSIGNOR T0 MINNIE MICHAELSEN, 01E' MIl'.\'.l'1\l'IE1APOLIS,v MINNESOTA..

ORE-PULVERIZER.

Learner.

Specification of Letters Patent.

Application led October 24, 1914. Serial No. 868,511.

vcertain new and useful Improvements in Ure-Pulverizers, of which the following is a specification.

My invention relates to grinding and pulverizing machinery, and especially to. machines for fine-grinding or pulverizing of ores preparatory to concentration, or separation therefrom of the valuable metalliferous constituents thereof. It is the object of my invention to provide a grinding or pulverizing machine wherein the final reduction of the material is eHeeted by a rubbing and rolling of its particles between a pair of'plates having parallel grinding or rubbing surfaces, the said plates being actuated so as to have a composite movement duringy which their adjacent surfaces move alternately toward and away from each other by very slight amounts,and also move to a much greater extent in directions parallel to each other, but oppositely and in alternating directions; so that the material between the plates is subjected to a moderate pressure insufficient to crush the same by direct compression thereof, and while Aunder'said moderate pressure is rolled or rubbed between the plates so as to bel disintegrated largely by the abrasive action of itsparticles upon each other.n` A further object of my invention is to provide, in connection` with the rubbing plates, means for constantly .feeding materials into the space between.the same, and means for causing the reduced material to be ejected therefrom at a rate proportional to the feeding and reduction' thereof. lA further object of my invention is to provide actuating mechanism for the pulverizing devices, arranged so that the rate of movement of the primary driving member is inversely proportional to the ,force or intensity of pressure that must be exerted by the pulverizing devices. at any instant, whereby the actuating force relquired for operating tlie machine will be substantially uniform. Further and more specific objects .of myv invention will appear hereinafter.

In ,the accompanying drawings, Figure 1 is a longitudinal vertical sectional view of,

a machine embodying my invention, the section being in the plane of the line .fr-# of Fig. 3, Fig. 2 is a side view `of the machine, with' the' adjacent fiy-wheel removed, Fig. 3 is a partial plan view of the machine, and partially a horizontal section on the plane of the line 1j-y of Fig. 2, Fig. 4 is a detailvertical sectional view, illustrating the action of the pulverizing devices, Fig. 5 is a side view'show'ing the saine parts in a diflerent position, Fig. 6 is a detail vertical section on the plane of the line a-e of Fig. 2, Fig. 7 is a detail horizontal section on the plane of the line 0-0 of Fig. 1, and Fig. 8 is a diagrammatic view of the rockingbeams, illustrating'the relative movements of the working-faces.

In carrying out my invention I employ a pair of rocking-beams mounted to oscillate about normally-fixed axes, and connected with each other so as to move simultaneously in like direction and through equal angles about saidixed axes. In the structure illustrated, there is a front rocking-beam 1 and a rear rocking-beam 2, which are mounted respectively on horizontal shafts 3 and 4, of which the aXes are parallel and lie in the same horizontal plane. Through the lower portions of the beams and at like distances from the respective shafts 3 and 4 are the link-shafts 5 and 6, of which the axes also ing-beams are disposed between the sidemembers 7 of a suitable frame. The frame side-members 7 are connected to each other at the rear end by a cross-piece 8 secured thereto by transverse bolts 9.' At the front end of the frame there is an upper crosspiece l0 secured to the side-members by large studs 11 and nuts 12, and a lower cross- 'ieee 13 which is secured to the sidememb rsby studs 14 and nuts 15.

The end-portions of the pivot-shaft 4: of the rear rocking-beam are journaled in suitable bearings 30 arranged in the frame sidemembers 7. At the ends of the upper crosspiece 10 are lugs 16 which extend into the front ends of horizontal guideways in the side-members 7. In saidguideways are disposed bearing-blocks 17 in which are journaled theends of the pivot-shaft 3 of the front rocking-beam. A plurality of plateshims' 18 are provided which -fit into the uideways adjoining the ends of the bearing-blocks 17, and which may be transposed from one end the other when it is deo lie in the saine 'horizontal plane. The rockframe side-members 7 passing through slots A in plates which partially close the inner sides of said chambers. The outer sides of said chambers are normally closed by hinged dcors 21, one of which is shown open in Fig.

2. On the ends of the link-shafts are bearing-blocks 22 and 23 which are retained in transverse position on the shafts by lcollars 24 secured on the shafts at the inner ends of the blocks, and plates 25 -secured on the ends of the shafts, as shown in Fig. 6. At each side of the machine the bearing-blocks 22 and 23 are connected to each other by a rectangular link 26 formed by a continuous metal strap. The bearing-blocks are disposed in the ends of the link and are held against the same by a spreader- 'device comprising a threaded rod 27 and end-blocks 28 and 29, the latter being threaded to receive the threaded end of the rod. For 4adjusting the bearing-blocksto positions closer to each other, the spreader-device is 'shortened and suitable plate-shims are placed between the sides of the bearing-blocks and the ends of the link. The links 26 receive alltensile stressesbetween the shafts 5 and 6,- while any compressive stresses between said shafts are received by the spreader-devices.

For causing oscillatory movements of the rocking-beams about the .axes of the shafts 3 and 4, a toggle-mechanism is provided comprising the front links 31 and rear links 32,y the vfront links being connected with intermediate portions of the shaft 6, the adjacent ends of the front and rear links being connected with a transverse intermediate shaft 33, and the ends of the rear links 32 being connected with a transverse shaft34 of which the ends are jou'rnaled in bearings 35 disposed in the lower rearward end of the frame side-members 7. A`

also employed as driving pulleys and arev connected by belt with a suitable source of power.

Between the adjacent sides of the rocking-beam there is a throat-like space into which the material to .be operated uponis fed by gravity from a hopper 41 which 4is disposed above the upper ends of the beams as shown. The throat .is lined with, and the working-faces of the beams thus formed by, renewable members which are secured to the respective rocking-beams, and of which the structure and arrangement are different at different parts ofthe throat, according to the specilic character of -the operations performed in the respective parts of the throat. The lowest part of the throat is formed by the rubbing-plates 42, which are madev of suitable hard and durable material `such as manganese-steel or chromium-steel.-

The faces o-r adjoining sides of the rubbingplates are parallel to each other'and quite close together. On' the back sides 4thereof -are ribsl43 which litA into channels extend- "the notches in the ends of the ribs, as shown in Fig. 7, and thus retain the plates securely upon the rocking-beams. 0n each' rocking- 100 beam, immediately abo-ve the respective rubbing-plates and forming the .intermediate side-portions of the throat, there are a series of feed-plates 45-whic'h are disposedalternately in a piled -re'lation .with spacing- 105 plates 46, the edges of all the plates engaging the face of the beam, but` the plates 46 being narrower than the plates 45 so Ithat,

there are rectangular transverse open spaces or channels between the Iedges of the latter adjoining the throat. The upper side-portions of the throat are formed by filler- 4'blocks 47 which are disposed above the feedplates and spacing-plates, the upper ends of said filler-blocks being in proximity to lugs 48 at the upper ends of lthe rocking-beams.A Through said lugs are passed screws 49 which engage the upper ends of the blocks and press the same and the plates 45 and 46 down against' shoulders formed on the 120 faces of the beams at the level of the upper edges of the rubbing-plates. `Rods' 50 extend vertically through coincident openings in the blocks 47 and the plates 45 and 46,

-to hold said parts in fixed transverse, relation to each other. The plates 45 are made of hard material, similar to that of the rubbing-plates 42, but the plates 46 and blocks 47 may be-made of softer and less expensive material, such as ordinary cast-iron or eaststeel. The sides of the upper] and intermediate portions of the throat, formed by the blocks 47 and the edges of the plates 45, converge slightly so that thethroat is widest 5 at the upper end and becomes gradually narrower toward the lower part, while at the bottom between the rubbing-plates the sides of the throat are substantially parallel.

In Figs. 4 and 5 the rocking-beams are le yshown in the two eXtreme positions between which theymay be moved by the togglemechanism. rlhe positions o f the beams shown in Fig. 4 are those assumed when the toggle-links have the greatest deflections above or below a plane passing throughthe axes of the shafts 6 and 34, and, for convenience in the description, said positions of the beams will be designated as the vertical or normal positions thereof. rllhe .positions of the beams shown in Fig. 5 are those assumed when the toggle-links are horizontal, or when the axes of the shafts 6, 33 and 34 all lie in the same plane, vand said positions of the beams will be designated as the tilted or inclined positions thereof. The

driving .'eceentrics are so arranged that the toggle-links are moved equal distances above and below the horizontal position, .so that during each revolution ofthe driving shaft the rocking-beams will be moved twice each way between the vertical and the inclined positions thereof.

In Fig. 8 the line A indicates a horizontal plane passing through the axes of the pivote shafts 3 and 4; the line B indicates 'a similar plane passing through the axes of the shafts 5 and 6; and the lines C and D indicate planes passing respectively through the axes Vof the shafts 3,and 5, and through 410 the axes of the shafts 4 and 6; all when the beams are in the normal vertical positions thereof. The working-faces of the rubbingplates42 are parallel with the planes C and D, and in Fig. 8 it is assumed for convenehience that both sides of the throat are parallel throughout, itbeing apparent that the movements of the actual working-faces, relatively to each othe, will be the same as those of the assumed parallel faces. rlhe rocking-beams are soconnected with each other, by the'links between the shafts 5 and 6, that the planes A, B,-C and D of the shaft-axes form a parallelogram in any position to'which the beams may be moved, both beams rotating about their pivotal axesinv the same direction and through equal angles. The positions of the planes when the beams are in a tilted or inclined position are indicated by the lines B, C' and D', and the angle m between the lines C and C is equal to the angle n4 between the lines D and" D. LFrom Fig. 8 it will be apparent that the working-faces of the beams, or the sides of the throat, will be farthest apart when the e5 beams arein. vertlcal position, or when the is equal to .0183 inches, or slightly less than planes C and D are perpendicular to the planes A and B; and in moving to an inclined position the distance between the Working-faces, measured perpendioularly thereto, will decrease in a definite mathematical relation to the angle of rotation of the beams about the axes 3 and 4. It will also be apparent that as the beams move toward the inclined position the workingface of the rear beam will move in an upward direction, while the face of the front beam will move in a downward direction; said movements resulting in a. rubbing action, or displacement of the workingfaces, relatively to eachother, in parallel but opposite directions; and that the amount of such displacement will have a definite mathematical relationvto the angle of rotation. rlhe first-mentioned movement of the working-faces relatively to each other may be designated as the closure, while the movement inparallel planes may be designated as the rub. The actual amounts of closure and rub of the working-faces, in any particular instance, may be expressed by the formulas Closure-:R versin fm. RubzR sin m rub of the working-faces are directly pro- Apoi-tional, respectively, to the versed-sines and the sines of the angles of rotation. Now the values of the sines of small angles is ver y much greater than the values of the versedsines of the same angles, and consequently, by limiting the rotation of the beams to very small angles it is possible to obtain a considerable rubbing movement of the workingfaces, together with an appreciable and definite but very slight closing movement thereof. For example, if the dist-ance between the pivotal axes were 30 inches, and the angle of rotation were 2 degrees, the closure would be 30 versin 2, or 30X.00061, which llO two-hundredths of an inch of closure; 'while the rubbing movement would be 3O sin20, or 30 .0349, which is equal to 1.047 inches, or slightlybmore than one inch of rub. The exact ratio of closure to rub, in this instance, is 1:57. It will now become apparent that, since it is necessary for effective action of the mechanism to have a certain minimum amount of rubbing movement of the working-faces, and as it is desirable` to have the ratio 0f closure to rub'very low, it is advantageous to dispose the pivotal axes of the beams as far apart as practicable. By so doing the desired amount of rubbing movement may be attained. by rotation of la() the beamsthrough a smaller angle than if the pivotal axes were closer together, because 1n a series of decreasing angles the values of thev versed-sines decrease much more rapidly than the values of the sines of the respective4 angles, so that with the smaller angle of rotation the closure will be less proportionally to the rub. Thus if the pivotal axes were 15 inches apart (instead of inches as in the first example), and it were desired to have the same amount of rub as in the rst instance, it 'would be necessary to rotate the beams through an angle of 4 degrees, at which the closure would be .0366 inches (versin 4=.00244) instead of .0183 inches, and the ratio of closure to rub would be 1:2812` instead of `1: 57. In other words, the closure would be twice as great for the same amount of rubbing movement.

Coming now' to a consideration of the action of the working-faces of the rockingbeams upon the materials in the throat between them, it should be noted that the materials operated upon are in a' granular condition .when fed into the throat; the ore, if originally in large masses, being previously crushed or broken into pieces of moderateA `size such, for instance, that the largest might pass freely down th throat to a position betweenthe plates 45. Now it will be seen that when the throat is filled with material of this character the slight closing movements of the working faces will be insuflicient to cause much pressure upon the material 'in those portions of the throat where the mass of material is of considerable thickness, since the granular mass is capable of being compressed to a slightly smaller bulk by the applicationV of only moderate pressure upon the same. -In the lower andnarrower parts of the throat the pressure will be greater, since the mass of material is' of less thickness, the volume of the intersticialv spaces into which the particles may be displaced is less, and yet the reduction of volume per unit of area is vthe same as in the wider-portions Aof the throat. Consequently, it appears that the pressure upon the material at any particularpoint will be approximately proportional to the width of the throat at such point, or that the pressure will be greatest between the plates 42, and will'be very slight or even inappreciable at the upper part ofthe throat between the blocks 47. The upper part of the throat, then, serves practically as a con. tinuation of the feed-hopper, to direct the material into the intermediate parts of the throat where the reducing action begins. In the intermediate portions of the throat the material is subject to slight pressure,

and is caught by the projecting edges of the plates 45v so that the granular particlesv are rolled and rubbed agalnst each other by the rubbing movements of the working-faces. The rectangular transverse channels in the working-faces, between the edge-portions of theplates 45, become lled with particles of the material as shown in Fig. 4, which tend to -support said edge-portions of the plates. The material in said channels serves also as a part of the workin -faces and minimizes wear and abrasion o the plates. each oscillation of the beams a portion of the material' is carrieddownward by the plates 45 and thus forced into the space between the rubbingfplates 42. Between the.

latter plates the material is subject to a greater pressure than before, and the rubbing and abrasion thereof is continued with' greater energy; but, owing to the slight movement of closure, the pressure is st ill insuicient' to directly crush the material, so that practically the entire reduction of the material is effected by the rubbing and abrasion thereof and the attrition of its particles Vupon each other, while the pressure upon rocking-beams to movement thereof becomes greater as the beams approach the extreme tilted or inclined position shown .in Fig. 5, since at this time the pressure onthe material in the throat is greatest, resulting in thek maximum friction of the material upon the working-faces and of the pivot-shafts and links-shafts upon their bearings.` But in the movement ofthe rocking-beams toward the above position the toggle-links approach the intermediate position, at which the links.

are in horizontal alinement with each other,

Also, at v the y and where the mechanical advantage of the toggle-mechanism is greatest. Thus the resistance offered by the driven part of the toggle-mechanism during various parts of the cycle of movements is aproximately equalized, and the force that must be applied thereto to actuate the same is substantially uniform. Y

Now, having described my invention, what I claim and desire to secure by Letters Patent is:

1.' In an ore pulverizing machine having a pair of rocking means, a shoulder on the inner face of each beam, rubbing plates secured to the beams below theshoulders, a

plurality of crushing members supported at the lower ends ofthe rocking means by lsaid iso shoulders and said rubbing plates, and means for clamping the-'crushing members together and forcing the same into support-` ing engagement with said shoulders to secure the crushing members against accidental displacement.

2. In an ore pulverizing machine having a pair of rocking beams, a shoulder on the inner face of each beam, a plurality of crushing members located above said shoulders, spacing plates located betweeneach adj acent crushing member for spacing the same, said spacing plates being narrower than the crushing members so as to provide channels between the edges of the crushing members,

4 and means for clamping said crushing members and spacing plates together and Jforcing) the same into engagement with said shoulders to securely hold the same on the beams. y

3. In an ore pulverizing machine having a pair of rocking beams, a shoulder on the inner face of each beam, a plurality of crushing members located above said shoulders, spacing plates narrower than the crushing members, located between said crushing members to space the same and provide channels between the edges of the crushing members, means for clamping said'crushing members and spacing plates together and forcing the same into engagement with said shoulders to securely hold the same on the beams, and rubbing plates `secured to said beams below said shoulders.

4. In an ore pulverizing machine havin a pair of rocking beams, a shoulder on the 1nner face of each beam,vsupporting plates secured to said beams below said shoulders, a plurality of crushing members mounted on each beamabove 'the respective shoulders spacing plates located between the crushing members, and means extending through the respective crushing members and spacing plates to hold the same together and firmly support the same on the respective shoulders.

In testimony whereof l have hereunto subscribed my name .in the presence of two wit-y .nesses CHAS. O. MICHAELSEN.

Witnesses:

GRACE V. SoMERs, G. HAsLEHURsT.

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