US2514538A - Vibratory power mechanism - Google Patents

Description

July 11, 1950 E. E. DEISTER 2,514,538

VIBRATORY POWER MECHANISM Filed Aug. 9, 1946 4 Sheets-Sheet 1 14 [a 1% l H y/ INVENTOR.

20 [MIL I. PEAS 72K.

July 11, 1950 E. E. DEISTER VIBRATORY POWER MECHANISM Filed Au 9, 1946 4 Sheets-Sheet 3 INVENTOR. fM/L E. Df/JTEE.

fli rafi/vzrs July 11 1950 DE|$TER 2,514,538

VIBRATORY POWER MECHANISM Filed Aug. 9, 1945 4 Sheets-Sheet 4 ,& INVENTOR.

fM/L E, 05/57:.

k &\\\\\\\\\\\ l 136 Patented July 11, 1950 VIBRATORY POWER MECHANISM Emil E. Deister, Fort Wayne, Ind.. assignor to Deister Machine Company, Fort Wayne, Ind.

Application August 9, 1946, Serial No. 689,604

3 Claims.

This invention relates to a vibratory power mechanism.

The chief object of this invention is to provide mechanism utilizing rotary power and transforming same to reciprocatory power through the use of rotary unbalanced Weights, the rotational axes of which are coincident so that the relative arcuate angularity between weights can be readily adjusted tooth-by-toth over a wide range so that the general direction of reciprocation can similarly be adjusted over a comparatively wide range, all without requiring any adjustments of other mechanism to be vibrated by said first mentioned mechanism.

The aforesaid permits a, shaking screen structure of this general type to be utilized for the segregation of different size solids of different materials, that is, materials of different specific gravities, such as gravel to be sized, broken coal to be sized, ballast to be sized, etc.

In other words, only relative arcuate adjustment of the coaxial weightsis required to adapt the present invention for the separation of any one of the materials so that the shaking screen operates at maximum efficiency for each such material and also without screen clogging.

The chief feature of the present invention resides in the coaxial mounting of the weights and thearcuate adjustment thereof for the purposes set forth.

Other objects and features of the invention will be set forth more fully hereinafter.

The full nature of the invention will be understood from the accompanying drawings and the following description and claims:

In the drawings Fig. l is an end view of a.

Fig. 6 is a transverse sectional view taken on line 6-6 of Fig. and in the direction of the arrows.

Fig. 7 is a transverse sectional view taken on line 1-! of Fig. 5 and in the direction of the arrows.

In the drawings, see Figs. 1 and 2, there is illustrated an outer frame '9 comprised of spaced angles suitably connected together and from which rise'supports I0. An overhead frame H is adjustably supported by these supports and its biased face i2 has secured to it a motor l3 having shaft M mounting pulleys l5 driving belts I6.

Within the frame is the shaker structure represented by a frame I! to which in overhead relation is secured an overhead base 3 mounting the agitator device to be more fully described. The agitator device includes the pulleys l9 driven by belts l6.

The shaker frame I! is cushioned upon the outer frame 9 throughout the shaker frame length by supporting springs '20, see Fig. 1. The shaker frame is slightly less than the outer frame as to length and narrower. It is of less height than uprights ID. The screen material is tensioned upon the shaker frame by adjustable yielding catches or connections 2|.

Fig. 2 illustrates a diagrammatic representation of the screen structure. Herein screen 22 receives all the material to be sized. Assume the same passes inch or smaller material. This falls through to lower screen 23 that passes only inch or smaller material. The, material trapped by screen 22 is caused to travel to and across screen 24 which passes 1% inch or smaller material. The lateral discharge from screen'24 obviously is greater than 1 inch.

Such material as passes through screen. 24- obviously is 1% or less and greater than 54; inch. Screen 25 below screen 24 passes inch or smaller size. Thus the material passed through screen 25 is no greater than inch nor less than inch.

The overrun obviously is sized between 34' inch and 1% inches. The overrun (centrally disposed) from screen 23 is less than and greater than inch. Thus material supplied to the screen structure at the upper left hand end, see Fig. 2, will produce five sizes thereof.

It is well known that substantially horizontally disposed screens, suchas indicated at 22, .23, 24 and 25 will function properly and efiiciently, without clogging, if the general direction of agitation is that required for the specific material to be separated. v

Herein such adjustment is readily effected in the agitator device proper, to which attention will now more specifically be directed. Same. is shown more fully in Figs. 3 and 4.

In Figs. 1 and 3 it will be observed that there is suitably secured the main housing members 26 and 21. Housing member 26 includes two end plates 26a and 26b and these provide certain inwardly directed stop shoulders 28a and 28bwhich confront each other and central apertures 29a and 29b.

The main housing portion includes the central bore 260 and mounted therein are the anti-friction elements 3!] and 3!. Shaft 32 is rotatably supported by the bushing structure 33 within the bearing and is suitably retained therein as indicated' The end of this shaft, which projects beyond the housing 26, has secured to it as at 34 the multiple pulley structure I9 aforesaid and a Weight 35, the latter being of cylindrical type with the chamber portion 35a formedytherein.

The shaft 32 aforesaid is enveloped-by a sleeve 36 which is operatively associated with the oil fiinger spacing sleeve 3'! and the anti-friction element 3!, the latter being retained in position by the lock ring structure 38. i

The sleeve shaft or tube 36 is provided with a k way 361;, and a cylindrical weight 39 having the chamber 39a therein is keyed as at 46 to said sleeve and secured by means of the lock screw Al which may be of the headless type. Herein a second weight, generally similar to the previously mentioned Weight, is provided, and the same is indicated by the numeral 42 keyed by the element 40 and locked by the screw 93, but this particular weight, instead of being charnbered as at 39a, has an I section as indicated at 42a.

The sleeve shaft 36 adjacent its opposite end mounts similar weights 42 and '39 in reversed relation, and same are keyed and locked to the sleeve, as previously described. The housing 2! ;includes the end plate 21a and the opposite end plate 211).

T he shaft 32 is extended beyond the housing 21 and mounts on the end thereof as at'M the cylindrical weight 45 chambered as at 435a, same corresponding to the similar weight 35 chambered at 35a. If desired, the pulley structure 19, shown integral in Fig. 3, may be detachably connected bythesame means 34 that the weight i 35 is secured to said shaft. This then would only require slightly longer bolts and would permit utilization .01 identical end weights, and for purposes herein these weights may be considered identical although actually for production purposes the two weights as aforesaid are only similar.

It will be noted that the central portion of the housing '21 includes the central bore portions 210 and seated therein are the anti-friction ,structures lfiand 47. 'The anti-friction structure I r that bearing a the Weight 45; as at 5,2, is a gear 53'. "This gear 53 meshes with a gear 54 mounted on one 'end'of a'jack shaft 5.5 antia frictionally supported as at .56 in a bore 51 parallel to the central bore 21c in the main housing p ru sJ" 3 Mes-hing with the gear '54 is another gear 58 mounted-e 1 anflther shaft 53, not shown-in Fig. 3 shown in Fig. 4. This shaft is antii-frice l e l l PP9 t i a ra l. bor indica d 4 at 60. The shaft 59 carries'at its other end a gear 6| which meshes with the gear carried by the sleeve shaft 36.

Rotational power is transmitted by shaft 32 through gear 53, gear 54, shaft 5%), gear 6| and gear 50 to the sleeve shaft 36 to rotate the last named in a direction opposite to the direction of rotation of the central shaft 32 and at a rate proportional thereto. 1

It will be noted that the gears *are' detachably mounted, -although having spline connection, on the ends of the jack shafts and 59. It will also b .noted that the cover plates 21a and 2111 are detachably mounted upon the main housing structure 21.

' -Thus whenever it is desired to adjust the relative angular displacement of the shaft 32 with respect to the sleeve shaft 36 the adjacent pulley may be removed, the cap plate 21a removed, and the gear 54 removed and the sleeve shaft 36 rotated an arcuate distance of one or more teeth and then the gear 54 replaced and the other .parts replaced in the reverse order.

* .Whenever it is not expedient to make the adjustment from the rear end, the end plate 21b is removed after the locking screws have been retracted from the weights and the same have been shifted axially toward the other end of the structure and the cover plate has similarly been shifted.

When sufficiently shifted, the gear 6| may be removed from its shaft 59 and the weights turned in the advance or retrograde direction an arcuate distance equal to one or more teeth.

Then the gear 61 is reapplied, cover 21b reapplied, andthe weights 39 and 42 shown in the right hand portion of Fig. 3 are also repesitioned axially and locked as aforesaid. The result is that the sleeve weights will be arcuately adjusted relative to the shaft weights.

It'will also be obvious that the sleeve shaft and central shaft are concentric and are coa-Xially mounted. The weights are mounted so their axes of rotation are coaxial and the weights are generally mounted in opposition the degree or extent' thereof being variable and further that such variation is readily accomplished, as previo-us-ly set forth.

By way of further explanation it is to be noted that as the two shafts are rotated centrifugal force is equally effective 0n the weights carriedby the respective shafts so that through the gearing illustrated at some intervals in the rotation'the centrifugal force of all weights iseffective in the same diametric direction, and at another period the same is effective in that same general direction but in an opposite sense.

Thus maximum centrifugal force incident to the summation of centrifugal forces produce a reciprocatory force, as it were, for effecting screen reciprocation since this force is only dissipated through the housings 26 and 2,1 which are carried by the base portion 18, in turn secured to the shaker screen frame structure II.

Now when the weights of the two shafts are in direct opposition and they are substantially of equal force and effect, reference being had to the relative velocities as well, the base I8 is not subject to' agitation or reciprocation and therefore in a cycle of agitation the force from the maximum recedes to a minimum and then increases to the maximum and obviously the num-' ber of oscillations or reciprocations cf the screen structure depends on the speed imparted to th vibratory device by the motor I3.

It furthermore will be quite clear th'at the only result of shifting the relative arcuate spacing of the weights, as it were, is to shift the relative general direction of the maximum reciprocatory force. Thus it is possible to obtain agitation along lines or directions from close to horizontal to 45 or more degrees therefrom as required by the character of the material to be handled, for reasons assigned aforesaid.

Generally the range of adjustment is between 20 and 60 degrees so that the component of the force that is transverse to the plane of the, screens insures the material dropping through them if of lesser size than the screen capacity, and the horizontal component of the forcev insures horizontal travel of the material not passed by the screen toward the discharge or overrun edge thereof, such as is found at the right hand end of screen 23, 25 and 24 and wherescreen 22 passes material to screen 24.

Obviously the general direction of agitation, insofar as the screen shown in Fig. 2 is concerned, should be upwardly and to the right. This means that the material is agitated so that smaller material freely passes through the screens and the other material not so passed is caused to advance horizontally and also upwardly so as not to clog the screens.

It is to be understood that the diagrammatic representation shown in Fig. 2 is merely given by way of example and that the specific mounting of the screen tructure within the main frame is also given by way of example only and that the invention is primarily directed to a method of vibrating shaking screen means through coaxially mountedunbalanced weights rotating in opposite directions, the coaxial mounting resulting in the attainment of maximum vibratory action without the generation of inherent opposing actions such as occur with oppositely rotating unbalanced weights having parallel shafts of rotation.

Reference will now be had to Fig. 5 wherein a modified form of drive between the driving shaft and the driven tubular shaft or sleeve is illustrated.

In Fig. 5 numerals of the I series indicate parts similar to or like parts in the previous figures and designated by the respective primary numerals. In this figure it will be observed that the sleeve I53 is keyed as at I52 to the shaft I30.

This sleeve is provided with a facial spline structure I 5311 and the shaft is suitably supported by the housing or main structure I21 through a bearing structure I41.

Within the housing is a, similar bearing structure I46 and at the opposite end thereof, and the same rotatably supports the sleeve shaft I36 to which is suitably secured the sleeve weight or weights I39, same being keyed to the sleeve shaft, as shown, and set screw locked together, as indicated at I4I.

The sleeve shaft extends into the housing I21 and through the bearing I46 and i provided on its end with a toothed arrangement I49 that confronts the toothed arrangement I53 although the two are logitudinally spaced apart.

The general similarity of the two structures to the extent the second embodiment has been thus described will be obvious. The driving connection and the adjustability, however, of the second embodiment does differ considerably from that shown in the first embodiment; hence, en'- tirely new numerals designate these parts Interposed between the two bearings I46 and at its opposite end is provided with a spline I85. I10 is provided with aseries of teeth, sockets or .the like such as shown at I86. locking screw sufficiently retracted for non-lockformation I14. One splined arrangement is associated with the splined structure I530. and the other splined arrangement I14 is associated with the splined structure I49 on the end of the tubular shaft. Both of these sleeves I12 mesh with a plurality of beveled pinions I15.

Herein two of the same are illustrated and more may be provided if desired. The two illustrated are diametrically arranged and a ring I15a includes radially directed shaft portion I16 that rotatably support said beveled gears.

The shafts I16 terminate in head structures I 11 and, if desired, see Fig. 6, there may be interposed between the beveled gear and the shaft an anti-friction structure I10. The adjusting ring I10mounts the heads I11 as at I and a pin or lock I8I may secure the same in assembled relation.

From the foregoing, therefore, it will be understood that if the central shaft is rotated the sleeve -I53 is rotated and by reason of the spline connection the beveled pinions I15 will be rotated upon their axes when the outer sleeve I10 is fixed to the housing I21.

As a result the other beveled gear I13 will be rotated, and by reason of the spline connection I14-I49 the sleeve shaft concentric and coaxial with the central shaft will also be rotated at the same rate as the central shaft but op- .positely.

,. Rotational ower is transmitted by central shaft I30-I32 to clutch member I 5|, keyed at I52, clutched at I53a'-I41 to crown gear I13 meshing with pinions I 15 rotatable on axes transverse to the central shaft axis. These pinions mesh with the opposed crown gear 112- I13 in turn clutched'at I41-I49 to the sleeve shaft I36 so that the two shafts rotate at the same rate but'in' opposite directions.

- The weights I39 and I45 carried by the sleeve shaft and the central shaft respectively will be variously disposed, that is, angularly adjusted, and the adjustment is obtained as follows, see Figs. 5 and 7: the housing I21 is provided with a threaded opening I03 that threadingly mounts a locking screw I84 having a locking projection The outer periphery of the outer sleeve NOW with the ing and with, for example, a wedge interposed between the weight I39 and the housing I21 to holdthe sleeve shaft stationary, rotation of the central shaft weight will affect rotation of the outer sleeve I10 to the desired degree.

:operatiohj It will be perfectly clear that the other end of the embodiment shown in Fig-,5 can besimilarl-y modified or the left end portion'lof Fig. 3, support fer the coaxial shafts may be duplicated in; the embodiment of the invention including that form shown in Fig. 5;

Sincethe mechanismherein has. beenso fully described and its operation has been equally fully described, it will be apparent, that the method of vibrating a shaking screen will. be mere'or less obvious from the aforesaid. so. that no'further detailed description is believed necessary; relative thereto;

While the invention has been illustrated and described in great detail in the drawings and foregoing description, the same is to be considered as illustrative.

The forms described herein as well as others which will readily suggest themselves to persons skilled inthisart, all are considered tobe within the broad scope of the invention, reference being had-to the appended claims.

The invention claimed is:

l. A vibratory device of the longitudinally balanced-coaxial type comprising a pair of oppositely rotatable concentric shafts, each of appreciable length, to wit, at least five times the. diameter thereof, the inner shaft projecting at'opposite ends. beyond the ends of the outer shaft, an eccentricall-y disposed weight at each projecting end of said inner shaft, an inner pair of axially spaced external bearings disposed inwardly of and contiguous to the ends of the said outer shaft for the rotative support of the same and into which the said outer shaft projects at opposite ends, another and outer pair of axially aligned spaced external bearings disposed immediately contiguous to the first mentioned bearings and inwardly of and adjacent the ends of the inner shaft for the rotative support of the same, a plurality of eccentrically disposed weights carried by the said outer shaft and inwardly of the inner the outer shaft and interconnecting said shafts for the simultaneous rotation thereof and in opposite directions, a portion of the gearing being annularly adjustable for effecting relative arouate displacement of the shafts for vibration direction variation, a pairof spaced housings, each enclosing a pair of adjacentbearings, said housings constituting the sole support for the device, the gearing being enclosed Within one of the housings and the rotating means being disposed 1 beyond the other housing.

2. A vibratory device of the longitudinally balanced coaxial type comprising a pair of opposite- 1y rotatable concentric shafts, each of appreciable length, to wit, at least five times the diameter thereof, the inner shaft projecting at opposite 1 ends beyond the ends of the outer shaft,'an eccentrically disposed weight at each projecting end of said inner shaft, an inner pair of axially spaced external bearings disposed inwardly of and contiguous to the ends of the said outer shaft for the rotative support of the same and into which the said outer shaft projects at'opposite ends, another and outer pairflof axially aligned spaced external bearings disposed immediately contiguous to the first mentioned'bearings and inwardly of and adjacent the ends of the inner shaft for the rotative support of the same, a plurality of eccentrically disposed weights carried by the said outer shaft and inwardly of the inner pair of bearings and. disposed in balanced axial relationrrelativeto. the length of said outer shaft, meansfor rotating an exposed portion of one of said shafts, and, gearing disposed at One end of the outer shaft. and. interconnecting. said shafts for the. simultaneous. rotation thereof and in opposite directions, a. portion. of the gearing being annularly, adjustable for effecting relative arouate displacement of the shafts. for vibration direction variation, said, gearing comprising a jack shaft andtwo sets of gears, one gear of each set being, associatedtherewith,and one gear of one setbeing'associated with the outer shaft and one gear of the other set being associated with the inner shaft, one of the jack. shaft gears being detachablef for annular adjustment purposes.

, 3. A vibratory device of. the longitudinally balanced coaxial type comprising a pair of oppositely rotatable concentric shafts, each of appreciable length, to wit, at least five, times the diameter thereof, the inner shaft projecting at opposite ends beyond the ends of the outer shaft, an eccentrically disposed weight at each projecting end of said inner shaft, an inner pair of axially spaced external bearings disposed inwardly of and continguous to the ends. of the said outer shaft for the rotative support of the same and into which the said outer shaft projects at opposite ends, another, and. outer pair of axially aligned spaced external bearings disposed immediately contiguous to the first mentioned bearings and inwardly of and adjacent the ends of the inner shaft for the rotative support of the same, a plurality, of eccentrically disposed weights carried by the said outer shaft. and inwardly of the inner pair of bearings and disposed in balanced axial relation relative. to the length of said outer shaft, means for rotating an exposed portion of" one of said shafts, and gearing disposed at one end of the outer shaft and interconnecting said shafts for the simultaneous rotation thereof and in opposite directions, a portion of the gearing being annularly adjustable for effecting relative arcuate displacement of the shafts for vibration direction variation, said gearing comprising a differential gear set with a pair of confronting ring gears, at least one pinion gear therebetween, and an annularly adjustable support for the pinion gear, and means for locking said support in the adjusted position, the axis of the pinion gear being transverse to the axis of the confronting gears.

EMIL E. DEISTER.

REFERENCES CITED The following references are of record in the file of this patent:

' UNITED STATES PATENTS Number Name 7 Date 1,323,329 Snyder Q. Dec. 2, 1919 1,827,586 Keefer Oct. 13, 1931 1,879,923 Deister Sept. 27, 1932 2,127,317 Wel'ch- Aug. 16, 1938 2,144,382 7 Lincoln et al'. Jan. 17, 1939 2,188,482 Parks Jan. 30, 1940 2,200,724 Robins May 14, 1940 2,294,448 Coyle et a1. Sept. 1, 1942 2,312,477 Pollitz Mar. 2, 1943 2,325,248 Johnstone July 27, 1943 2,367,070 Symons Jan. 9, 1945 FOREIGN PATENTS Number Country Date 567,084 Finance" Dec. 1, 1923

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