US2586161A - Mechanical counting device - Google Patents

Description

Feb. 19, 1952 w. E. HASTINGS 2,586,161

MECHANICAL COUNTING DEVICE Filed Aug. 16, 1946 6 Sheets-Sheet 1 E a i ii 571 527??? Ward E1 Has Lz'n s 27g 4,07 WM Feb. 19, 1952 w, HASTINGS 2,586,161

MECHANICAL COUNTING DEVICE Filed Aug. 16, 1946 6 Sheets-Sheet 2 Feb. 19, 1952 W. E. HASTINGS MECHANICAL COUNTING DEVICE 6 Sheets-Sheet 5 Filed Aug. 16, 1946 WIIIHJIJIJIIHHI llllllll HI IE ll O Q P wm i om g m mN IHHHIIII I H \Q fi-z/enfar Ward Has [v 5 Feb. 19, 1952 w. E. HASTINGS ,5 6

' MECHANICAL COUNTING DEVICE Filed Aug. 16, 1946 6 Sheets-Sheet 4 [Iii 5272272 Mra E. Has Zz'nys Feb. 19, 1952 w. E. HASTINGS 58 MECHANICAL COUNTING DEVICE Filed Aug. 16, 1946 6 Sheets-Sheet 5 Ward Effasfiy by -Z/%;/%MM

Feb. 19, 1952 w, HASTINGS 2,586,161

MECHANICAL COUNTING DEVICE Filed Aug. 16, 1946 6 Sheets-Sheet 6 IN VEN TOR. M/Zrd E 1%slz' gp Patented Feb. 19, 1952 UNITED STATES PATENT OFFICE MECHANICAL COUNTING DEVICE Ward E. Hastings, Chattanooga, Tenn., assignor to The Chattanooga Medicine 00., Chattanooga, Tenn., a corporation of Tennessee Application August 16, 1946, Serial No. 691,116

8 Claims.

This invention-"relates to a'device for the continuous subdivision and segregation into equal portions of particulate or other flowable mate rial continuously delivered frm a machine pro ducing such material. A specific form ofthe de-" vice of the present invention is adapted for attachment to a rotary tablet press of conventional type for use in filling bottlesor other receptacles with equal number of tablets produced by said press.

The device of the present invention comprises a chute or other conduit for receiving the products of a tablet machine orthe like in the form of a stream of tablets or other particulate or flowable material. This chute is provided with uct are efiected alternately into each of said a blade pivoted at one edge and located in said a chute above a bifurcated channel leading to sep arate containers or receptacles. The blade is interposed in the path of the products or particles delivered from the-tablet press or other producing device and, by reason of a periodic alternation in its angular position, acts to divert the product first to one channel and then to another, the channels delivering the'product to suitable receptacles.

The blade is actuated by a mechanism including a drive gear connected directly to or driven directly from the main drive shaft or other moving part of a tablet press or, the like. Said drive gear, in its turn, actuates a series of gears that finally actuate a cam shaft having a cam acting on pivoted contactors that operate to actuate two solenoids alternately. The snap action of the solenoids is transmitted through a link system into a sudden reversal of the angular position of the diverting blade pivoted within the chute;

Included within the train of gears connecting the initial drive gear with the gear attached to and driving the cam shaft is 'an exchangeable gear wheel turning on an idle stud movable in an are so that gears of various sizes may be substituted to change the ratio of actuation without disturbing the operative connections between the various members of the gear train.

It is, therefore, an important object of the present invention to provide an adjustable measuring device adapted to be driven directly from a tablet press or the like or its source of power and capable of diverting the stream of products produced by said tablet pressor the like alternately into each of two channels at intervals exactly synchronized with the delivery of the machine so as to subdivide said product into equal portions of any desired size deposited alternately at two stations.

Another important object of the present invention is to provide a measuring device adapted for use in any type of producing mechanism that delivers a continuous streamof particulate or other" flowablematerial-and capable of direct driven connection to said producing device by means including a gear train having' one replaceable channels during successive periods.

Other and further objects and features of the present invention will become apparent from the following detailed description and appended claims taken in conjunction with the attached drawings which show, by'way of example, a conventional tablet-making machine provided with a measuring device according to the present invention. More particularly? Figure 1 is a fragmentary side elevational view, with parts shown in section, and other parts broken away, of a measuring device according to the present invention attached to' a conventional tablet-making machine, only two sets of opposed upper and lower table'punches being shown;

Figure 2 is a transverse horizontal cross-sectional view taken along the line II-II of Figure 1, with certain parts broken away and other parts shown in section otherwise than along the line II-IL'and showing molds for a complete set of tablet punches;

Figure 3 is a greatly enlarged'side'elevational view taken along the line III--III of Figure 1 and showing one side of the gear train of the device of Figure 1 together with supporting means therefor; I

Figure 4 is' a greatly enlarged side elevational View taken along the line IVIV of Figure 1, and

showing the other side of'gear train anda porwith the chute and its pivotedblade;

Figure 8 is a wiring diagram of the electrical circuit of the device of Figure 1; and

Figure 9 is a viewsimilar to Figures 5 and 6 but showing the lever or link system in still another operating position.

As shown in Figures 1 and 2, the structure there illustrated includes a 'tablet-pressof conventional construction having 'a frame it supported. by a base (not shown) and carrying a table II having a stationary spindle I2 mounted thereon for supporting a rotating head generally indicated at l5. The latter is formed with a number of radially projecting rings or annular disks alternately superimposed with smaller rings or neck portions in between forming a structure of several stories and of diameters to suit the coactin mechanism. More particularly, the head l5 includes a lowermost worm gear [5a axially apertured around its periphery to receive vertically reciprocating lower tablet punches IS; a constricted portion |5b formed with peripheral grooves l5c permitting reciprocation of the lower punches l6; a middle portion l5d of greater diameter holding tablet molds IT; a constricted portion or neck l5e; and an uppermost portion I5 of greater diameter axially apertured around its periphery to receive the vertically reciprocating upper tablet punches I8. The spindle I2 projects above the upper portion l5 of the head [5 and carries above the latter a collar 20 having a cam ring 2| fitting grooves l8a in the upper punches l8 to reciprocate the latter. vertically as the head I5 is rotated. A cam track 22 is provided on top of the table I l to reciprocate the lower tablet punches I6 as the head 15 is rotated.

Powdered material is fed into the molds I1 and there compressed between the punches I6 and [8 to form tablets which are then ejected upwardly by the lower tablet punches l6 while the upper tablet punches [8 are withdrawn upwardly. The ejected tablets are collected at a fixed point in the rotation of the head l5 by means including a gutter 25 (supported by a bracket 26 from the table II) provided with a finger 21 projecting in over the mold-carrying head part l5d to intercept the ejected tablets and cause them to pass over the gutter 25 and to fall into a chute 28 having a screened bottom 28a for separating dust from the finished tablets.

The head I5 is driven from a shaft 30 y means of a worm 3| meshing with the worm gear 15a. The shaft 30 may be journaled in bearings 32 supported by suitable means (not shown) from the frame I6 and may receive its power from any suitable source, for instance, through a pulley and belt assembly 33.

It will be apparent that in the above-described conventional tablet press the rate of flow of tablets through the chute 28 is directly proportional'to the speed of rotation of the driving shaft 30.

As best shown in Figure 1, that portion of the present device operative to effect the actual segregation of the stream of tablets falling through the chute 28 into equal portions is supported from the'base In by means of a horizontally extending bracket 40; a plate 4! affixed to the top of the plate 40 and having an outer depending flange 4| a; another horizontally extending plate 42 having an inner depending flange 42a opposed to but spaced from the other depending flange Ala; and a vertically extending plate 43 projecting above the two plates 4| and 42 and clamped between the depending flanges Ma and 42a by a bolt and nut 44.

As shown in Figures 1 and 2, the pressed tablets fall from the chute 28 into a box 56 afiixed to the outside of the upper end of the plate 43. The box 50 terminates downwardly in two divergent funnels 5i and 52 terminating in spouts such as 52a each adapted to discharge,- into a separate container such as a bottle 58 disposed on the plate 42. A plate 54 serves to rigidify and hold apart the funnels 5i and 52.

The stream of tablets falling through the chute 28 into the box 50 is alternately diverted into either one of the funnels 5i and 52 by knife blade 60 having its lower edge pivotally disposed to the table II.

at the bottom of the box 50 between the openings into the two funnels 5| and 52 (see Fig ures 5, 6, and 9). More particularly, the knife blade 68 is formed of sheet metal or the like bent back upon itself into narrow V-shape and provided with cross pieces 60a across both ends of the V-shaped, otherwise o'pen sides of the knife blade. The cross members 60a are attached to a rock shaft 6! projecting through suitable apertures on both sides of the box 56 and journaled in bearings 62 affixed to the outside of the box 50. On that side of the box 56 turned toward the tablet press, the shaft 6! projects beyond its journal 62.

Means are described hereinbelow for synchronizing the pivoting of the knife blade 60 with the production of tablets by the tablet press, so that an equal number of tablets will alternately be diverted into the two funnels 5! and 52 by the blade 60. These means include a train of gears- (see Figures 1 to 4) supported from the frame In in spaced relationship thereto by a vertical plate 65 having a horizontal portion 65a attached The outer upper margin of the plate 65 is provided with aligned bearings 66 for journaling a shaft 61 extending in parallelism with the upper edge of the plate 65. Below the space between the two bearings 66, an idle stud shaft 68 projects from the plate 65 on the same side as the bearings 66. Near the lower margin of the plate 65, and more or less in vertical alignment with the interspace between the bearings 66 and the stub shaft 68, still another stub shaft 69 projects from both sides of the plate 65. To the right of its two shafts 68 and 69 and at an intermediate level, the plate 65 is pierced by an arcuate slot 10 for'movably receiving an idle stub shaft H. The slot 10 is everywhere concentric with the shaft 68, so that the shaft II will always be at the same distance from the shaft 68.

Referring now to Figures 1 and 2, it will. be noted that adj acently the pulley 33 the main shaft 30 is provided with a gear wheel 15 meshing with a gear wheel 16 attached to an end of the shaft 61 projecting beyond the plate 65, for driving the shaft 61 from the main shaft 30. As shown in Figures 2 to 4, a worm H is affixed to the shaft 61 between the bearings 66 and drives a worm gear 18 rotating on the shaft 68 and having a hub 18a for spacing the gear from the late 65. The worm gear 18 is integrally united to a smaller gear wheel 19 by means of a collar 80, which, along with the gear wheel 19, is free to rotate on the. shaft 61. The unit formed by the worm gear 18, its hub 18a, the collar 86, and the gear wheel 19 is held on the shaft 68 by means of a cap 8! affixed to the end of the shaft 68 by a screw 82.

The gear wheel 19 meshes with a gear wheel 83 rotatable on the shaft H and united to a. smaller gear wheel 84 through a collar 85 in-- tegral with the gear wheels 83 and 84. A cap 86 holds the unit formed by the collar 85, the two gear wheels 83 and 84, and a hub 8 a for the gear wheel 84 (for spacing the latter from the plate 65) on the shaft 1 I, being attached to thefree end of the shaft by means of a screw 81. The slot 10 being concentric with the shaft 68, the

. slgtft (I can be moved alongthe slot without loss of meshing engagement between ;.the 1 gear: wheel I9 and the gear-wheel 83. Suitable .means. are provided for clampingthe shaft in any desired position in the slot 10.

The shaft 69 'has removably attached thereto a gear wheel90-meshingwith thegear wheel84l The gear wheel 90 may have any desired number of teeth, depending upon the frequency required for actuation of the pivoted blade 90. The gear wheel 90 is spacedfrom the plate by a hub 98 and held on the shaft 69 by a cap! and a screw 92.

Means for translation of rotation of the shaft 59 into pivoting movement-of the'blade includes a contact mechanism. More particularly, the shaft 69 projects through the plate away from the gear wheel 90 to actuate a contact mechanism on the other side of the plate as-best illustrated in Figure 4. As shown in the latter figure, and also in Figure 1, the contactor mechanism is enclosed within a generally circular housing 95 open on one side and having on the otherside a fixed bottom portion 96 (oflelectrically insulating material) in the form of a sector of a circle approaching a semicircle-in size. This sector rests upon and is connected to a hub-like housing portion 91 that spaces the sector from the plate 65 and is formed so as to accommodate freely the projecting end of the shaft 09. An insulating plate 98 of the same shape as the plate 95 is angularly movable in the bottom of the housing 95-opposite the plate 95. The plate 95'carries a-fixed contact bracket I00 having a contact point I00a, while the plate carries afixed contact bracket IOI havinga contact point mm. A cam, I02 is'carried by the free end of'theshaft 69 and is capable of moving over the corner margins of the plates 96 and 98 to actuate successively, on rotation, a pivoted contactor I03 on the plate 90 having a contact point I 03a adapted to coact with the contact point I00a and another pivoted contactor I04 on theplate 90 having acontact point I00a adapted to coact with the contact point IOIa. The shape of the cam I02 is such that, on rotation, the cam i will cause one pivoted contactor to close and then to break one electrical circuit and thereafter cause the other contactor'to close and break another circuit. Further, the cam is so shaped as to permit rotation in both directions.

The two contactors I03 and I04 are both connected in series to one electrical conductor wire I05 through flexible conducting means I03!) and I002), respectively, while the two contactors I00 and IOI are connected, respectively, to electrical conductor wires I06 and I01. The wires I05, I05, and I0? enter the housing through "a conduit I00.

The separation of the positions at which the pivoted contactors I03 and I04 just close or effect electrical contact is theoretically angularly about the cam I02, but actually this position may not give exactly equal intervals of operation of the measuring mechanism; For

this-reason, the plate 98 can be angularlyadjusted (to effect the segregation of exactly equal: amounts by the measuring mechanism) and held adjusted position, as by a finger I09apro jecting in over the plate 98 from the housing 95 and carrying a screw I09.

Wires IIO lead from the contactors within the housing 95 to a mechanism for pivoting the blade 60 including solenoids III and H2 affixed, re-- spectively, to upwardly projecting portions i Ita and I I la of vertical plates H3 and I I 4 (see Figuresdtox'l and.9) having their lower edges fixedly resting on. the. plate 4|. The platesiI I3 and II 4 are. connected .attheir ends by means of cross plates II5and IIB held together by screws II! to form an elongated rectangular framework parallel withthe plate 43. The solenoids II I and H2 straddle the two ends of this framework, and the solenoid cores I I3 (of solenoid III) and MS (of solenoid II2) are free to reciprocate downwardly below the solenoid coils into the interspace between the bars I I 3 and I I4.

The solenoids I I I and 'I I2 actuate a rock shaft I22 extending through the middle of the plates H3 and H4 and journaled in bearings I23 on the outside of said plates. More particularly, the rock shaft is actuated through an interlocking link system (shown in Figures 5 to '7 and 9) including two irregularly contoured members I 20 and I2I extending in parallelism between the plates I I4 and i It and keyed to the shaft I 22 and an upwardly bent elbow-sha ed link E25 overlying the member I20 tog-ether with another upwardly bent elbow-shaped link I20 overlying the member I2 I. One end of the link I25 is pivotally connected to the solenoid core II 8 at 520, While the other end of the link I25 pivots on a stub shaft I 29 attached to the plate I I0, One end of the link I25 is pivotally connected to the solenoid core H9 at I30, while the other end pivots on a stub shaft I3I attached to the plate II3. Thus, when the solenoid H2 is energized, the solenoid core H9 moves upward carrying with it that end of the link I26 pivotally attached to the core II9, while the other end of the link I26 pivots about the shaft I3I. When the solenoid III is energized, the solenoid core IIB moves upward, carrying with it that end of the link I25 pivotally connected to the core I I8, while the other end of the link I25 pivots about the shaft I29.

The link I29 is formed on the right lower side with a projecting spur I25a capable on upward movement of the link of engaging a spur I2Ia on the member I2I. The other low-er side of the link I26 is formed with an upper shoulder I26!) and 'a-lower shoulder I250 separated by a surface I26d which shoulders are adapted to engage a spur I2Ib extending'from the member I2I in the opposite direction from the spur I2 Ia. The'other member I20 and link I25 are shaped similarly to the member I2I and the link I20. Thus, the member I20 is formed with spurs I201: and I201), while the link I25 is formed with a spur I25a and shoulders I25?) and I250 separated by a surface I25d as described in connection with the other member I20 and link I25.

The coaction between the solenoid I I2 with the core IIO, the link I26, and the member I2I will become apparent from an inspection of Figures 5, 6, and 9. Figure 5 shows the solenoid core II9 withdrawn'from the solenoid II2, the lower right-hand'end of the link I20 resting on the plate 4|, and the member I2I tilted over to the right with the spur I2 Ib resting on the shoulder I201). When the solenoid core I I2 is energized, the link I26 pivots around the shaft I3I, the link end pivoted to the core H9 at I30 being raised. During the initial rise of the right-hand end of the link I26 (before the spur I26a engages the spur I2 Id) only the link is lifted, and the shoulder I261) is lifted away from the spur I2ib, to permit tilting of the member I20a to the left on further upward movement of the link I26. Such further upward movement of the link effects engagement of the spur I20a with the spur I am, with a consequent tiltingxof the member I2I to the left so that the-spur I2Ib comes to rest against the shoulder I260, as shown in Figure 6. It will be noted that in this position, the member I2I is locked within the link I26. When the solenoid H2 is de-energized, the core H9 and the link I26 drop down into the position shown in Figure 9 wherein the spur I2Ib still rests on the shoulder I260, but the terminal surface of the spur I2Ib now rests against the surface I26d between the two shoulders I26b and I260, thus holding the member I2I against leftward movement. When the other link I 25 (actuated by the solenoid core II8) goes through the same cycle of movements, shaft I22 is tilted to the right, carrying with it the member I2 I. Then the spur I2Ib slides over the surface I26d and is seated against the shoulder I26b as the link I26 descends to the position shown in Figure 5.

It will be noted that the above-described members I and I2I together with links I and I26 form an interlocking device serving as an actuating means between the solenoids III and H2 and the shaft I22, to insure snap actuation of the shaft I22, to lock the members I20, I2I and the links I25 and I26 together when not actuated by the solenoids, and to eliminate all oscillation of the shaft I22 when the solenoids are not actuated.

The shaft I22 carries, outside the plate I I3 and the bearing I23 attached thereto, a generally horizontal rocking arm I35. Links I36 have their lower ends pivotally connected at Ia to the ends of the rocker arm I35 and their upper arms pivotally connected at I36b to a crank I3! affixed to the free end of the shaft 6I projecting through the box 50 and the plate 43.

Each solenoid III and H2 has one terminal connected to one end of a tilt-type mercury switch I'disposed on the upper surface of the rocking arm I35, so that the contactors, in making contact, pass the current through the mercury switch to the solenoids. As the solenoid is energized, the linkage previously described tilts the mercury switch and immediately breaks the contact to release the solenoid while the contactors are still in contact in their respective positions. Thus the provision of the tilt-type mercury switch permits the use of a slow moving cam to make contact, the breaking of the circuits being made rapidly. As a result, the contact points are assured of long life, no large sparks are formed on openin of the contacts, the solenoids are energized only for a short period of time, and the wear of the mechanism will be minimized, being effected solely by the slowly moving cam.

The electrical circuit is shown diagrammatically in Figure 8 as including a wire I05 connected to the one pole of a source electricity (not shown) and branching out to the contact points I03a and I04a which are thus connected in parallel. From the contact point I 00a cooperating with the contact point I03a, a wire I06 leads to one end of the mercury switch I40, while another wire I01 leads from the contact point IOIa cooperating with the contact point I04a to the other end of the mercury switch I40. In the latter, current can flow through the mercury (when the switch is tilted to the left) from the wire I06 to a wire I (of which the coil for the solenoid III is a part), while current can flow through the mercury (when the switch is tilted to the right, as shown in Figure 8) from the wire I07 to a wire I46 (of which the coil for the solenoid I I2 is a part). Both the wires I45 and I46 are connected to a wire I41 leading to the other pole of said source of electric power.

It will be noted that the pivoting of the blade 60 is strictly synchronized with the production of tablets in the tablet press, for the shaft 30 driving the tablet press also drives the mechanism actuating the blade 60 and including, in sequence, the gear wheel I6 (driven by the gear wheel (5 on the shaft 30), the shaft 61, the worm H, the worm gear 18, the gear wheel 19, the gear wheel 83, the gear wheel 84, the gear wheel 90, the shaft 69, the cam I02 actuating alternately the pivoted contactors I03 and I04 to energize alternately the solenoids III and H2 that alternately rock the shaft I22 in opposite directions through the agency of the links I 25 and I26 and the pivot members I20 and I2I, the rock arm I35 (affixed to the shaft I22) the links I36, the crank I31 and finally the rock shaft 6i on which the blade 60 is fixed. The rate of actuation of the pivoted blade is determined by .the ratios of the various gears ahead of the cam I62, for the rate of revolution of this cam determines how often the solenoids are energized to actuate the link system serving to pivot the blade 60. This ratio of actuation can be varied by substituting various gear wheels having different numbers of teeth. Note that the shaft H can be adjusted in various positions in the slots I0 so that the gear wheel 84 can mesh with various gear wheels 90 of different sizes without disturbing the meshing engagement between the gear wheel 82 and the gear wheel 83.

An example is given as follows of the method of calculating the ratio of actuation of the pivoted blade for a gear wheel 90 having a given number of teeth.

If there are sixteen tablet molds I! in the head portion I5d and the latter includes a gear wheel I5a having 52 teeth which in turn is driven by a triple-thread worm 3I, then the main shaft 30 will make 52:3=17 revolutions while sixteen tablets are being produced or 52 revolutions while 48 tablets are being produced. If the gear wheel 15 on the shaft 30 has 48 teeth, and if the gear wheel I6 on the shaft 61 has 52 teeth, the shaft 6'! will rotate 48 times While 48 tablets are being produced, which makes the ratio one tablet for each revolution of the shaft 61.

If the worm TI on the shaft 61 is a singlethread worm driving a 50-tooth worm wheel 18 rotating as one with a 25-tooth gear wheel 19 driving a IOU-tooth gear wheel 83 rotating as one with a 50-tooth gear wheel 84 in turn driving an exchangeable gear wheel 90 having a permissible minimum of 25 teeth and a permissible maximum of 125 teeth, we find that for the minimum and maximum number of teeth in the gear wheel, the ratios are, respectively, as follows:

1 X 2 5 X 50 l revolutions of change gear per tablet 50X lOOX 125 500 Since electrical contact occurs twice for each revolution of the shaft 69 on which the exchangeable gear 90 is mounted, and since such contact is the point of origin of the actuation of the pivoting means for the blade 60, it follows that for the exchangeable gear having 25 teeth, the number of tab-lets produced between alternations in position of the blade 60 will be :2:50, while for a gear wheel 90 having teeth the number of tablets produced between alternations in position of the blade 60 will be 500:2:250.

Further changes may be made by altering the ratios between, for instance, 15 and I6. For in- 'stance, -if-gear 1s has ioi ieetir in iead orisz,

the tablet counts for each alternation imposition= of theblade- 60' wil1-"be doubled so that an exchangeable-gear having '25 teeth would count lOOtablets and an exchangeable gear tfl having 5 125 teeth would count 500 tablets.

It is also possibleto use -a wide-faced exchangeable gear llflmeshing with-the gear-'83 instead of with the gear 84 in which case the count (with the gear 16 having 104-teeth) wouldbe 1o 50 tablets per alternation when the gear 96 has i 25 teeth. -It-wi1lthus be seen that various means may beemployed to obtain actuation ofthe electrical circuit at proper intervals,- without sacrific- Accuracy of counting depends not only on precise timing of the pivoting'ofthe blade-6l but also on the type of interruption of thestreamof falling particles or other flowable material. The

manner of interruption-is important because in 20* the stream of falling particles, particularly when the falling particles are relatively large, the particles tend to react irregularly-when impinging upon any surfaeein their path,- certain particles tending to bounce one way and other particles tending to bounce another Way. It is apparent that the surface presented to such impingement at the moment when the blade -65) pivots should be as small as possible, and that the time within and it is therefore not mypurposegto limit the patent granted on this invention otherwisethan necessitated by the 'scopeof the appended claims.

I claim as my invention:

-l.- In---a mechanical counting device for particu1ate--=material, a box-like structure having verticallyextending lateral wallsdefining a main {flow channel for receiving'a stream of saidpar- ----ticulate-material, means for delivering said particulate material to said mainflcwchannel during normal operation of the device, means moving proportionally to the delivering means, V- sha'ped mea-ns closely adjacent thelower extremity of--the box-like structure dividing said main ing-precise equalization of segregated quantities. 15

flow channel into two separate flow channels, a

rockshaft -journaled in opposed lateral walls of saidbox-like structure adjacent the lower-extreinity-of the box-like structureand projecting iexternallyof the box on one side, a sharp-edged -bla'de-secured to said rockshaft within said box- --like structure, acrank on said rock shaft ex- Which such impingement could possibly occur should be as short as possible. i It is for this reason that I have provided a thin relatively sharpedged blade pivoted at-its lower edge and capable of cutting rapidly through the stream of falling particles to provide a sharp cut-off point separating those particleswhich have been travelling in one direction from particles which are to travel in the other direction. In this connection, attention is directed to the operation of the posed in said conduit above the point of bifurcation 50 as to be capable of diverting said stream into either one of said twochannels, means for pivoting said blade including a rock shaft, means solenoid-link system that actually efiectspivotl ing of the blade 6%. Note that when, for instance, the solenoid core H9 is energized to lift the link [2%, the "initial movement of the link l'26 (up to the point where the spur 126a engages the spur I2 a from below) involves only overcoming the weight of the link I26 and the core H9 which permits rapid acceleration. Further upward movement of the link I26 under the influence of the core H9 is resisted only by friction, for the for translating tilting movement of said rock shaft into tilting movement or said plane, a level system for operating said rock shaft including first and second lever means for alternately tilting said shaft, respectively, in a first angular direction and in a second and opposite angular direction, said first lever means being capaoleof locking said shaft against any tilting at the moment of termination of said tilting movement and tilting of the member i2! and the lifting of the link 52%? rock the shaft 122 permits the link'l25 and the core I Hi to drop and permits the member l2il to tilt. Hence, the link or lever system-snaps quickly from one position to another to 'tiltthe of holding said rock shaft against tilting in said second direction before initiation and after termination of said tilting movement, and separate electrical means for actuating said first lever means and said second lever means.

3. In a mechanical counting device for particulate material, a conduit for receiving a main blade fill to divert the falling tablets from one55 funnel to another. Further, at the termination of each solenoid action, the spurs I201) and -l 2lb (pointing in" opposite directions) rest, respectively, on the shoulders [25b and I260 to lock the shaft 522 against oscillation and prevent bouncing of the blade 66. Note also that as the rocker arm I35 is tilted when one of the solenoids is energized, the mercury switch l 49 on the rocker arm tilts therewith, thus breaking the circuit enstream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels, a pivoted blade dis- 'posed said conduit above the point of bifurcation so as to be capable of diverting said stream into either one of said channels, means for pivoting said blade including a rock shaft, means for translatingtilting movement of said rock shaft ime tilting-movement-of said blade, a lever sysergizing the solenoid as soon as the solenoid has moved a predetermined distance. This action occurs rapidly and permits only a brief fiow of current upon the closing of the electrical circuit by one of the pivoted contactors. There is, therefore, no tendency to arcing or burning at the contactors, which might give rise to faulty action.

Many details of construction may be varied within a wide range without departing from the principles of this invention and without sacrificing the advantages mentioned hereinabove,

tem for operating said rock shaft including first and second lever means for alternately tilting said shaft through a limited are, respectively, in

a first angular direction andi'n a second and opposite angular direction, said first lever means being capable of locking said shaft against any tilting at the moment of termination of said tilting movement of said rock shaft and of holding said rock shaft against tilting in said first direction before initiation and after termination of said tiltingmo'vement, said second lever means --bei-ng capable of locking said shaft against any --tilting at the moment of termination of said tilt- 11 ing movement and of holding said rock shaft against tilting in said second direction before initiation and after termination of said tilting movement, separate electrical means for actuating said first and said second lever means, and

switch means actuated by said rock shaft for terminating the actuation by said electrical means of said two lever means when said rock shaft has been tilted over a predetermined arc in said first angular direction and in said second angular direction.

4. In a mechanical counting device for particulate material, a conduit for receiving a main stream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels, a pivoted blade disposed in said conduit above the point of bifurcation so as to be capable of diverting said stream into either one of said two channels, means for pivoting said blade including a rock shaft, means for translating tilting movement of said rock shaft into tilting movement of said blade, first and second rocker members on said rock shaft, first and second one-armed levers overlying, respectively, said first and said second rocker and pivoted, respectively, one on each side of said rock shaft, said levers being capable on upward movement of tilting said rockers over a predetermined limited arc toward the pivoted ends of said levers and of locking said rockers against tilting in any direction at the moment of termination of said upward movement, said levers further being capable of holding said rockers against tilting in the direction of the pivoted ends of said levers before initiation and after termination of upward movement of said levers, separate electrical means for actuating said first and second levers, and switch means actuated by the tilting of said rock shaft to terminate the action of said electrical actuating means when said rock shaft has been tilted by either one of said levers through said predetermined are.

5. In a mechanical counting device for particulate material, a conduit for receiving a main stream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels, a pivoted blade disposed in said conduit above the point of bifurcation so as to be capable of diverting said stream into either one of said two channels, a lever system for pivoting said blade alternately in opposite angular directions to divert said stream alternately into said two channels, electrical means for actuating said lever system, and switch means operated by said lever system for terminating the action of said electrical actuating means when said blade has pivoted through a predetermined arc in either one of said angular directions.

6. In a mechanical counting device for particulate material including a conduit for receiving a main stream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels and a pivoted blade disposed in said conduit above the point of bifurcation so as to be capable of diverting said stream into either one of said two channels and a lever system for pivoting said blade to divert said stream alternately into said two channels and electrical means for actuating said lever system, a mechanical timing means for said electrical actuating means including a gear train with adjustable ratio of action adapted to be syn- 12 of said product is effected into each of said channels at alternate periods.

7. In a mechanical counting device for particulate material including a conduit for receiving a main stream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels and a pivoted blade disposed in said conduit above the point of bifurcation so as to be capable of diverting said stream into either one of said two channels and a lever system for pivoting said blade to divert said stream alternately into either of said two channels and electrical means for actuating said lever system, a timing means for said electrical actuating means including first switch means for initiating operation of said electrical means, a rotatable cam for actuating said first switch means, a second switch operated by said lever system for terminating operation of said electrical means, and mechanical means for rotating said cam adapted to be synchronized with the delivery of said main stream whereby delivery of said product is effected into each of said channels at alternate periods.

8. In a mechanical counting device for particulate material including a conduit for receiving a main stream of said material bifurcated so as to be capable of delivering streaming material into either one of two channels and a pivoted blade disposed in said conduit above the point of bifurcation so as tobe capable of diverting said stream into either one of said two channels and wherein timing means synchronized with the delivery of said main stream of material is utilized for actuating the blade to effectuate delivery of said material into each of said channels at alternate periods, means adapted for pivoting said blade including a rock shaft, means adapted for translating tilting movement of said rock shaft into tilting movement of said blade, first and second rocker members on said rock shaft, first and second one-armed levers overlying, respectively, said first and second rocker members and pivoted, respectively, one on each side of said rock shaft,

- said levers being capable on upward movement thereof of tilting said rocker members over a predetermined limited arc toward the pivoted ends of said levers and locking said rocker members against tilting in any direction at the moment of termination of said upward movement, said levers further being capable of holding said rocker members against tilting in the direction of the pivoted ends of said levers before initiation and after termination of upward movement of said levers, and electric means controlled by said timing means for actuating said first and second levers.

WARD E. HASTINGS.

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

UNITED STATES PATENTS Hansen Sept. 9, 1941

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