US2829757A - Container feeding mechanisms - Google Patents

Description

April 8, 1958 R. BREEBACK CONTAINER FEEDING MECHANISMS 4 Sheets-Sheet 1 Filed Dec. 25. 1953 m b w W awn MN l w? d u 'R April 8, M R. H. BREEBACK 2,829,757

CONTAINER FEEDING MECHANISMS Filed Dec. 23, 1953 4 SheetsSheet 2 l INVENTOR.

Ry. olph J11 Bzyehaci,

BY Maw! M ATTORNEY-$1 April 1958 R. H. BREEBACK 2,829,757

CONTAINER FEEDING MECHANISMS Filed Dec. 23, 1953 4 Sheets-Sheet 3 a II l L 0 4b I v 7; E 86 95 1 V INVENTOR; 17 15 1 Rudolph J[. Br,ee,b,ack,

ATTORNEYS.

Za (2 Q jig Q April 8, 1958 R. H. BREEBACK 2,829,757

v CONTAINER FEEDING MECHANISMS Filed Dec. 23, 1953 4 Sheets-Sheet 4 I INVENTOR k1 I RadolphJ-fiflneehack,

MI JIQNWA ATTORNEYS.

United States Patent CONTAINER FEEDlNG MECHANISMS Rudolph H. Breeback, Baltimore, Md., assignor to Crown Cork & Seal Company, Inc., Baltimore, Md, a corporation of New York Application December 23, 1953, Serial No. 399,998

48 Claims. (Cl. 198--31) The present invention relates to container feeding mechanisms and, more particularly, to mechanisms for moving containers to and from filling machines. The invention also includes certain improvements in container supporting platforms of rotary filling tables. I

The feeding of bottles and cans smoothly between various machines in a bottling plant involves substantial difficulties, particularly if a single machine for performing one operation feeds containers to, or receives containers from, a plurality of machines for performing another operation. For example, if a filling machine is able to fill four hundred containers per minute, but it is necessary to deliver empty bottles thereto from two bottle washers or soakers, each with the capacity of two hundred bottles per minute, the two lines of bottles from the washers must be smoothly placed in a single line for delivery to the rotary filling table of the filling machine. The problem of thus combining lines of containers is tremendously increased when the merged line of containers must move at relatively high speed, for example, four hundred containers per minute. One aspect of the problem is that if the containers intermittently contact with each other while moving at such high speed, either cans or bottles may be upset and, if bottles are involved, they may be marred or abraded.

When the containers have moved from the filling machine, it may be necessary to divide them into two or more lines, each line going to a separate mixer, labeler or casing machine. Here again, the problem of effecting a smooth and quiet division is tremendously increased if the single line to be divided is moving at high speed.

Although the problems discussed have been stated in terms of containers and the embodiment of the invention hereinafter described discloses the mechanism designed for handling beverage containers, it will be understood that the invention is entirely applicable to the handling of articles other than containers and which are of various shapes and forms.

Various mechanisms heretofore have been proposed to handle the combining and dividing of containers or other articles. However, the arrangements heretofore proposed for the handling of containers are not entirely suitable for the handling of containers moving at the high linear speeds required by present-day filling machines or other bottling plant equipment. A particular drawback of previous arrangements is that the bottles or cans are very apt to be marred or upset during the transfer action. signed to divide or combine lines of articles other than bottles or cans moving at high speed are not applicable for the handling of bottles or cans, because bottles and cans are of relatively light weight and substantial height, but have a small base area.

Such mechanisms as heretofore have been de-' An' object of thepresent invention is to provide a' 2,829,757 Patented Apr. 8, 1958 with a minimum possibility of articles being marred, upset or jammed.

Another object of the invention is to provide a mechanism for transferring articles from a plurality of low capacity conveying elements to a single high capacity conveying element.

A further object is to provide a mechanism for transferring articles from a single high capacity conveying element to a plurality of low capacity conveying elements.

Still another object of the invention is the provision of a transfer mechanism which is so designed that once articles have been placed in a desired relative arrangement, for example, spaced apart, they will be maintained in that arrangement.

Difficulties arise if operation of a beer filler is stopped for a few minutes, as may be necessary if the supply of containers is temporarily interrupted at the washer. In more detail, when operation is re-started, several of the first round of containers filled usually will foam to a slight extent and may have to be discarded. Such foaming usually is due to the fact that the small amount of beer which remains in each filling head during the stoppage becomes very slightly warmer than the beer in the reservoir. Therefore, when the small charge of warmer beer moves into the bottle, foaming is initiated and may continue while the remainder of the fill moves into the bottle.

One feature of the present invention resides in the fact that the container feeding mechanism is so synchronized with respect to the rotary filling table that the containers supplied to the rotary filling table by either container supply ,line always will be placed on the same filling platforms of the rotary table. For example, if two infeed conveyor means are used, the containers moving from one conveyor means will be placed on even numbered filling platforms and those from the other conveyor means always will be placed on the odd numbered platforms. If one conveyor means, for example, that which provides containers for the even numbered platforms, fails to receive containers from the bottle washer or other source of containers, the odd numbered platforms nevertheless will receive containers in regular order and therefore will continue to fill those containers in normal fashion. If the stoppage of containers to the even numbered platforms continues for a sufficient length of time that foaming may occur when feed of containers to those platforms is resumed, the operator need only check the containers on the even numbered platforms. In the meantime, as stated above, the containers received by the odd numbered platforms all will be filled without difiiculty.

In comparison with the above-described regularity of action, it will be perceived that if a pair of conveyor means delivered containers at random, and if delivery by one conveyor means should be discontinued, some filling heads might produce a foam-fill over various lengths of time and every container would have to be carefully checked until after all conveyor means resume feed.

Another object of the invention is to provide a container feeding mechanism to deliver containers to a rotary filling table from two or more different sources and which mechanism is so synchronized with respect to the rotary table that containers moving from one source always will be delivered to the same series of platforms and filling heads of the rotary filling table.

Still another object of the invention is to provide a transfer mechanism for use with a rotary filling machine which is particularly effective in moving containers at high speed to a rotary filling table and without possibility of containers being upset.

Another object of the invention is to provide an improved form of container engaging and centering inech=- Figure 3 is an enlarged detail sectional view on the line' 3 3 of Figure l with portions broken away;

' Figure 4 is an enlarged detail vertical section on the line 44 of Figure 1;

Figure 5 is a view on the line 5-5 of Figure 1 showing a container supporting platform and a portion of a filling head of a rotary filling machine in elevation;

Figure 6 is an axial section of the lower portion of a filling head;

Figure 7 is a top plan view of a container centering P a Figure 8 is a plan view of a modified form of the invention; and

Figure 9 is a fragmentary plan view of a modified form of deflector for use with the present invention.

Referring to Figures 1 to 4, the mechanism there illustrated includes two bottle or can conveying elements 10 and 11 forming part of a first conveyor means. The elements 10 and 11 are straight line endless link-type conveyors formed of fiat plates and are suitably guided in the upper surface of a table structure 12. In the embodiment of the invention discussed below, each of the elements 10 and 11 would handle containers received through intermediate conveyors from a separate bottle washing or can rinsing apparatus.

A third bottle or can conveying element 13 included in a second conveyor means is of the same type as the elements 10 and 11 and extends beyond, parallel to and intermediate the conveying elements 10 and 11. In the arrangement under discussion, conveyor 13 is adapted to receive bottles or cans supplied by the conveying elements 10 and 11 of the first conveyor means. In Figures 1 and 2, the arrows A indicate the direction of travel of containers in the operation now under discussion of the structure of Figures 1 to 4. As shown by such arrows A, the conveying element 13 is arranged to deliver containers to the infeed dial 14 of a beverage filling machine and dial 14 then places the containers upon the usual vertically movable container supporting platforms 15 of the rotary fillingtable 16.

In accordance with usual practice, the rotary filling table 16 is journalled for rotation about a vertical axis, fixed with respect'to the filling machine base structure generally indicated by the numeral 17. Infeed dial 14 also is journalled for rotation in the base structure 17 and it will be understood that the right-hand portion of the conveying element 13 is suitably mounted in that base structure so that the upper run of element 13 will move across the top surface of the filling machine base structure or work table. In Figure l, the left-hand portion of this table is broken away.

The conveying element 10 delivers containers to a pocketed dial 20 rotatable above the upper surface of table structure 12. The other conveying element 11 delivers containers to a similar dial 21 also journalled in the structure 12. Both conveying elements 10 and 11 will have suitable stationary guides extending along their length and, immediately in advance of the dials 2t) v and 2 1, the respective conveying elements haveassociated therewith container spacing devices 22 and 23. These devices may be of the construction disclosed in the application for Article Feeding Mechanism of Carl L. Day. and Rudolph H. Breeback, filed June 6, 1951, Serial No. 230,192, now Patent No. 2,730,226, and are adapted'to progressively space apart containers moving in contact therewith. That is, each of the devices 22 and 23 is of screw form and is rotated about a horizontal axis substantially parallel with the elements 10 and 11. For example, during movement of a container upon element 10 along feed screw 22, the helical groove in the screw will control the container so that it will be spaced a predetermined distance from the immediately following container. As is described in said Day and Breeback application, and as is illustrated with respect to the structure associated with feed screw 22, in order to hold containers in contact with the screws 22 and 23, and also to stop operation of at least the adjacent feed screw in the event a container becomes jammed with respect thereto, a pivoted guide plate 24 is provided on the opposite sides of the conveying elements 10 and 11 from each of the feed screws Each pivoted plate 24 normally occupies a position such as indicated in Figure l, but if a container becomes jammed with respect to a feed screw, the corresponding plate will swing away from the feed screw and about its pivot 25 to thereby operate a switch as described in said application to thereby stop movement of at least that feed screw.

As has been indicated above, the dials 20 and 21 receive containers from the conveying elements 10 and 11. Because the screw 22 and dial 20. are symmetrically out of phase with the screw 23 and dial 21, the dial 20 will receive a container at a time point which is midway between the time points when dial 21 receives two immediately successive containers. The dials 20 and 21 deliver containers to an additional pair of dials designated 30 and 31. It will be observed that the dials 2t) and 21 are positioned on opposite sides of the center line of the conveying element 13 and the dials 30 and 31 are similarly positioned, the axes of the four dials being positioned at the corners of an imaginary rectangle. All four dials are of the same pitch diameter so that containers move about all of the dials on like radii. The dials 20 and 21 are shown provided with five equidistantly spaced pockets and, in such case, each of the dials 30 and 31 would be provided with ten pockets.

As will be clear from Figure 1, a container at position C1 in a pocket of the dial 21 and moving along stationary guide 34 will reach the position indicated at C2 where it will be under the control of dial 31 which will carry the container along a stationary guide 35 to position C3 where the container also will be engaged by a pocket of the dial 30. (The element D shown in Figure 9 would not be provided for use with the operation now under discussion, but would be installed for a modified operation subsequently described.)

While the dials 21 and 31 have been moving the container discussed immediately above, the dials 20 and 30 will be moving a container from position C4, through position C5 to position C6. It will be noted that the container at position C6 will be in the pocket of dial 30 which is immediately rearward of the dial 3% pocket occupied by the container at position C3. In short, (a) the dial 20 positions containers in alternate pockets of the dial 330, and dial 30- moves those containers to positions where they are engaged by alternate pockets of dial 31 while (b) dial 21 is delivering containers for engagement by the other pockets of the dials 31 and 30.

The pockets of the dials 30 and 31 move in registry and are so designed that containers moving therewith will have their vertical axes spaced in accordance with the spacing between the axes of containers on the platforms 15 of filling table 16 and that maintained by dial 14. In; order'to insure that the containers on conveyor 13 will be held uniformly spaced to this same extent, particularly during high speed operation, a feed screw 40. extends along one side of conveying element 13, a stationary guide plate 41 extending along the other side.

The feedscrew 4 0 is. of. the same type as the feed screws 22 and 23 except that itsv helical groove is of ste m uniform pitch throughout its length and the device ordinarily may be of substantially greater length than the feed screws 22 and 23. As is shown in Figures 2 to 4, feed screw 40 has its infeed end 45 extending between the upper and lower plates 46 and 47 of the dial 31, this end of the feed screw being provided with a stud element 48 which is journalled in a collar or socketed element 49 extending toward the feed screw from the journal assembly generally designated 50 described below. Referring to Figures 1 and 4, a standard 51 extends upwardly from the edge of the supporting structure 12 outwardly of the dial 31. A tube 52 extends horizontally through an aperture in standard 51, the tube 52 being held in adjusted position in the standard by set screws 53. Tube 52 extends between the upper and lower plates 46 and 47 of dial 31' closely adjacent to the dial hub 53.

A rod 54 fits in the inner end of the tube 52, rod 54 being firmly held co-axial with tube 52 by an arrangement such as indicated in Figure 4, including a journal sleeve 55 fitted between the rod and tube and a nut 56 rotatably secured to the rod and adapted to have threaded engagement on the exterior of the tube 52. At its inner end, rod 50 has the socketed element 49 welded thereto, the-axis of the socket recess 57 extending at right angles to the axis of the rod 54. Hence, the stud element 48, which is coaxial with feed screw 40, may extend into the socket 57.

The journal at the infeed end of feed screw 40 described above permits that feed screw to be readily aligned at any desired position with respect to the conveyor 13, the adjustment primarily being made by moving the tube 52 with respect to the standard 51. It will be noted that rod 54 may rotate on its axis and with respect :to tube 52 so that socket recess 57 can be aligned with the axis of feed screw 40.

. 6 the bottles will not fall over when they are placed upon the conveyor 65 by the washer. As is hereinafter described, the conveying elements 10 and 11 are operated at higher speed than the washer outfeed conveying elements 65. However, even tall bottles such as export beer bottles can be smoothly transferred to the conveying elements 10 and 11 by a fixed deflector such as 66 shown positioned at the outfeed end of 65 and the infeed portion of the conveying element 10 to deflect the containers from the relatively slow conveying element 65 to the faster conveying element 10.

The washer, the two conveying elements such as 65 and the corresponding conveying element associated with If the mechanism is to be used to handle a run of containers of a different size than that indicated in the drawings, the various fixed guides and the feed screws 22, 23 and must be moved either toward or away from the longitudinal center lines of their respective straight line conveyors. Also, it will be necessary to remove the dials 20, 21, 30, 31 and 14 and replace them with dials having pockets of the proper size. When it is necessary to remove the dial 31, this can be done by disconnecting the standard 51 of Figure 4 from the supporting structure 12 or, simply by freeing tube 52 from standard 51.

As best indicated in Figures 3 and 4, plates 58, formed of a material such as phenol-formaldehyde thermosetting resin such as Bakelite may be secured to the top surface of the upper plates 46 of all the dials to increase their height if tall containers such as nine-'and-a-half' inch, sixteen ounce export beer bottles are to be handled. The plates 58 increase the height of the dials so that the dials will engage such bottles at a point about five inches above thebottle base, thereby insuring that such bottles will stand upright at high speed.

It will be understood that the conveying elements 10 and 11 may 'be driven from a common shaft but, in any event, these elements will be driven in properly timed relation to the other elements of the mechanism and the filling table 16.

The operation of the mechanism described above is as follows: In the operation of a bottle washer, a line of containers, for example, twelve bottles, may be simultaneously placed upon each of two straight-line conveying elements respectively positioned to the left of the conveyor elements 10 and 11. In Figure l the outfeed end of such a conveyor appears at 65. As soon as the line of twelve bottles has been moved clear of the washer .by a conveyor element such as 65, another line of a like number of bottles will be placed upon conveying elethe conveying element 11 are generally operated at such speed as to maintain a line of contacting containers immediately adjacent the infeed ends of the feed screws 22 and 23 so that an adequate supply of containers for the filling machine will be assured.

The feed screws 22 and 23, dials 20, 21, 30 and 3-1 and the feed screw 40 are operatively connected by suitable gearing so that all of these elements will operate in synchronism at the relative speeds discussed below. All of the elements just mentioned preferably will be geared to the drive for the filling table 16 and dial 14 though speed changing arrangements may be interposed to permit independent adjustment of the speed of travel of the conveying elements 10 and 11 and also independent adjustment of the feed screws 22 and 23 with respect to the remainder of the elements. As is described in said Day and Breeback application, the feed screws 22 and 23 will be driven by gearing connected to their right-hand ends. The feed screw 40 also will be driven by gearing connected to its right-hand end.

Referring now to the relative speed of the elements shown in Figure 1, if the filling table 16 is operating to handle containers at a linear speed of 1200 inches per minute with the container axes spaced three inches apart, the conveying element 13 and feed screw 40, as well as the dials 20, 21, 30 and 31 will operate at that same linear speed. Under these conditions, feedscrew 40 will maintain the containers spaced on three inch centers and the pockets of the dials 30 and 31 will maintain containers on three inch centers but the pockets of the dials 20 and 21 will move containers on six inch centers.

Because the dials 20 and 21 are moving at linear speeds of 1200 inches per minute and handle containers spaced on six inch centers, it will be necessary for the conveying elements 10 and 11 and feed screws 22 and 23 to deliver containers to the dials 20 and 21 spaced on six inch centers and moving at linear speeds of the order of 1200 inches per minute. This requirement can be met by operating the conveying elements 10 and 11 at linear speeds of 120-0 inches per minute and rotating the feed screws 22 and 23 at such speed that their left-hand or infeed ends will advance containers at linear speeds of the order of 500 inches per minute, that is, approximately the speed of the conveying element 65 and the corresponding conveying element which delivers bottles to conveying element 11. By this procedure, bottles may accumulate at the infeed ends of the feed screws if, in accordance with usual practice, the output of the washer is slightly greater than the demand of the succeeding device or machine, in this case, the feed screw.

Because the container engaging helical groove of each of the feed screws 22 and 23 is of increasing pitch toward its outfeed end as described in said Day and Breeback application, when the infeed end of one of the feed screws is rotating to advance containers at a speed of the order of 500 inches per minute, the outfeed end of the feed screw will permit containers to move at a linear speed of the order of 1100 inches per minute. In other words, although the conveying element 10, for example, will be moving at 1200-inches per minute, it will merely slide beneath any containers standing adjacent the infeed end of the-teed screw 22 and when a container is removed from this group by the infeed end of feed screw '22,-thc container then will move at the linear speed permitted by the'infeed end of the screw 22, namely, 500 inches per-minute. While the containermoves along with the screw, the linear speed of the container will progressively accelerate due to the pulling action of conveying element and the permissive effect of the progressively increasing pit-ch of the feed screw 22.

At the instant that the container becomes completely free of the groove of feed screw 22, the container then will be free to move with and at the speed of conveying element 16. 'At this instant, a pocket of the dial will be advancing along its arcuate path toward the container under discussion. It will be noted from Figure 1 that rearwardly of each pocket of the dials 2t} and 21, the dial perimeter progressively curves toward the dial axis as indicated at 62. Therefore, when a container is free of the outfeed end of feed screw 22, the container will be free to move at the same linear speed as the conveying element 10 except as restricted by the portion 62 of the dial perimeter immediately in advance of the dial pocket which is to receive the container. Because the portion 62 progressively approaches the dial axis, the free container may advance somewhat with conveying element 10 but it probably will not achieve a speed of 1200 inches per minute until it actually is engaged by a dial pocket in the manner indicated 'by the container at position C4 in Figure 1. Once a container has been fully engaged by a dial 20 or 21, its linear speed will continue constant at the rate required by the filling machine. will be observed that once the containers move out of contact with each other at the infeed end of the feed screws 22 and 23, they will remain spaced apart so that marring of the containers will be entirely avoided.

It will be noted from Figure 1 that the spacing between the pockets of the dials 20 and 21 is greater than .that imparted by the threads of the outfeed end of the feed screws 22 and 23. However, with conveying elements 10 and 11 moving at a faster linear speed than that imparted to containers by the feed screws, a container released by a feed screw immediately will become spaced from the following container and when a dial pocket fully engages the outfeed container, this spacing will increase.

It will be noted from the above that although the output of the washers or rinsing devices may be only 200 containers per minute and feed screws 22 and 23 and conveying elements lit and 11 may handle containers at that rate, nevertheless, the outfeed of the dials 3t and 31 can be 400 containers per minute and containers outfcd from.30 to 31 will be travelling at a linear speed which is twice that of the conveying element and the corresponding conveying element which delivers containers to the conveying element 11.

It will be understood that the feed screws 22 and 23 may be designed to accept containers at a linear speed more closely approaching that of the conveying elements 10 and 11, for example, at 906 inches per minute if elements 1!) and it are moving at 1200 inches per minute. Also, the outfeed linear speed of the screws may more closely approximate the linear speed of 10 and 11. However, if the containers moving from a feed screw such as 22 are to be spaced on centers as far apart as six inches,

it appears desirable to free the containers from the feed from screw 40 in exact synchronism with the pockets of dial 14. The usual fixed guide plate 70.is secured adjacent dial 14, plate including a guiding edge 71 concentric with the dial axis and adapted to engage the Moreover, it

8 body portions, of containers thedialpockets, we I I In order to-further insure that the containers will be held steady and against vibration or upsetting during at least the latter portion of their travel with dial 14 and also during transfer from dial 14 to the container supporting platforms 15 of the rotary filling table, the invention provides the arrangement described below. As best shown in the upper right-hand portion of Figure l, a guide rod 72 is secured to a vertical post 73 extending upwardiy from the stationary table 17 of the filling machine. As best shown in Figure 5, guide rod 72 lies in a horizontal plane at such height that it will engage a container closely adjacent the container mouth. For example, Figure 5 shows rod 72' positioned to handle export beer bottles, and in such case, rod 72 will contact the bottles immediately below the mouth enlargement.

The portion 74 of rod 72 adjacent its free end 75 is curved to be concentric with the axis of dial 14 and on such a radius that containers moving in the dial pockets will be engaged by the rod at the height mentioned above. However, the infeed end 75 of rod 72 is bent to curve slightly closer to the dial axis to thereby provide a lead-in portion upon the rod.

The portion 74 of rod 72 which is concentric with the axis of dial 14 terminates at the imaginary line extending between the axis of dial 14 and the axis of the filling table 16 and, as shown in Figure 1, to the left of thatpoint, rod 72 includes a portion 76 concentric with the axis of the filling table 16: Portion 76 is only of sufiicient length to be engaged by containers on platforms 15 which are in their lowermost position, usually flush with the surface'of the stationary table 17 of the filling machine as indicated in Figure 5.

Each of the filling platforms 15 is provided with a container holder 80 which is about three inches high and of arcuate form to provide a slightly less than semicylindrical and vertically extending surface to engage at least the lower portion of the body of the container. If cans including a lower seam flange are to be handled, the container holder 80 would be recessed at its lower edge to receive the can seam. Each holder 80 is secured to its platform 15 by means of set screws 81 extending through slots in the base flange of the holder, the slots extending radially of the filling table.

Each platform 15 also will be fitted with two vertical rods 82 inwardly of the holder 80, each rod secured in an aperture 83 at the inner edge of the platform by a set screw 84. The upper end of each rod 82 is threaded as indicated at 85 and a container engaging plate 86 is supported at the upper ends of the pair of rods. The plate 86 is shown in plan in Figure 7 and includes slots 87 adjacent its inner edge adapted to fit the rods 82, the plate being clamped in adjusted position on the rods by means of opposed nuts 88. The slots 87 also will extend radially of the filling table.

The outer edge of each plate 86 is provided with a V-shaped notch 89, the inner and central portion of which is formed on a radius corresponding to the outside radius of the neck portion of a container. For example, if the plate 86' is to handle export beer bottles, the portion 90 of the plate 86 will be curved on a radius corresponding to the outside radius of the neck of such a bottle at the point immediately below the neck reinforcing shoulder. Because this surface of export bottles is slightlytapered to reduce upwardly, the portion 90 of notch 89 also would be similarly tapered as indicated by the dotted line 91 of Figure 7.

It will be noted from Figure '5 that when a platform 15 is in its lowermost position, the container engaging plate 86 of a platform 15 will lie in substantially the same plane as the container guiding rod 72. Therefore, so long as a container is on a platform at that position, its neck, and mouth portionwill be engaged between the rod 72 and the plate 86. At the same time, the base to hold them securely in portion of the container will be engaged by the container which the beer tube 99 of nozzle 100 is threaded. A

vent tube 101 inclines downwardly through adapter 96 and opens to the interior of the outer sleeve 102 of nozzle 100.

The exterior of the nozzle liquid tube 99 is reduced in diameter as indicated at 103 from a point opposite the lower end of passage 101 to ports 104 in the outer tube 102. By this arrangement, as a container is filled, gas and air therein may escape through the ports 104 and space 103 to move upwardly through the passage 101 to the reservoir. A separate passage, not shown, may open through adapter 98 to the space 103 for counterpressure flow. A container mouth sealing gasket 105 is positioned in the adapter 96' with its lower surface closely above the ports 104. It will be noted that no centering bell slidable on nozzle 100 need be provided when the bottle holding arrangements of Figure 5 are provided. Therefore, the nozzle 100 may be of maximum and uniform outside diameter down to its lower end. For example, with a bottle having a mouth bore of five-eighths of an inch, the outside diameter of nozzle 100 may be at. least one-half an inch. Also, its lower end may be rounded to center containers.

The operation of the bottle guiding rod 72, platform structure and filling nozzle of Figures 5 and 6 is as follows: While a container is moving with the filler infeed dial 14, or at least during the portion of its movement with that dial wherein the container moves from stationary table 17 to a platform 15, the container will be engaged not only by dial 14 and guide plate 70 but also by guide rod 72. Because guide rod 72 will engage the container adjacent its mouth, vibration of the container will be minimized. At the instant'that the container is firmly positioned against the container holder 80 on a platform 15, the upper portion of the container likewise will engage the inner portion 90 of the notch 89 of plate 86 and the mouth portion of the container still will be in contact with the guide rod 72. This position of the container with respect to the guide rod is indicated by the platform at position 15a of Figure 1.

As the rotation of the filling table 16 continues, the container will move clear of the infeed dial 14 but still will be engaged by the platform structure of Figure 5 and the guide rod 72. At the point in the rotation of table 16 where the platform 15 will begin to rise, slightly to the right of the position indicated by the platform 15b of Figure 1, the guide rod 72 extends sharply outwardly from the filling table 16 to thereby be clear of the rising movement of the container.

As is illustrated in Figure 5, the nozzle 100 of the filling head 95 has its lower end only about a quarterinch above the mouth of the container when the platform 15 is in lowered position. In order that the containers will be positively centered with respect to the nozzle 100 as soon as possible after the container moves clear of the guide rod 72, the filling machine will be provided with a platform controlling cam arrangement such as a disclosed in application Serial No. 260,968 of Carl L. Day and Rudolph H. Breeback, filed December 11, 1951, for Filling Machines, now Patent No. 2,699,282. The point to which the initially-acting step cam of that application will lift the container is indicated in dotted Ines at a in Figure 5 and this lift may be about one inch. With the mouth of the container in this raised' position with respect to nozzle 100, it will be impossible then will be raised at a slightly lower rate to bring the mouth of the container into engagement with the sealing gasket of the filling head.

It will be understood that if the containers to be handled are of less height than the export bottle illustrated in Figure 5, the guide rod 72 would be lowered and the mouth plate 86 would be correspondingly lowered to thereby engage the container immediately below its mouth.

It will be noted that because the container feeding mechanism of Figure 1 operates in synchronism with dial 14 and the rotary filling table 16, the containers supplied by one of the conveyor means such as 10 or 11 always will be positioned upon the same platforms 15 of a rotary filling table 16. For example, assuming that the rotary filling table 16' includes sixty filling heads and platforms, if the containers received from screw 22 and dial 20 are placed upon the even numbered platforms, those moving from the feed screw 23 and dial 21 will be placed upon the odd numbered platforms. This arrangement is particularly efficient with beer filling machines because if a charge of beer stands in a filling head for a few minutes, that charge becomes slightly warm and therefore is apt to foam in the first container which is filled when filling is resumed. By the arrangement described above, if feed of containers on the conveying element 10 is interrupted, the feed of containers on the conveyor 11, feed screw 23 and dial 21 may continue and, moreover, the same filling heads will be kept constantly in operation. When the feed of containers by the conveyor 10, feed screw 22 and dial 2% resumes, the first round of incoming containers all will be placed beneath the filling heads which are apt to produce a foaming fill and the operator need only concern himself with the containers moving from those platforms.

The invention also comprehends moving containers or other articles in a reverse direction from that discussed above, that is, from the filling machine or other source to two receiving points. If the mechanism of Figures 1 to 4 is operated in that manner to handle the output of a filling machine, the containers would move in accordance with the arrows B of Figure 1. In more detail, the containers would be removed from the filling table 16 by dial 14, functioning as an outfeed dial, and the containers would move from dial 14 to conveying element 13 and screw 40. Each container on conveyor 13 would be engaged by opposed pockets of the dials 30 and 31 as indicated at position C3 in Figure 1.

Immediately beyond this position, the stationary table 12 the guide plate 35 and would include a central tongue.

71 and lateral enlargements 72' and 73. As is usual with such devices, if the tongue 71 is extending upwardly as viewed in Figure 9 immediately after a container moving in the direction of the arrows B has passed position C3, tongue 71 will guide such container to dial 21. In such case, the lateral projection 73' will extend into the path of movement of .the container. As the container moves past projection 73, it will swing or press the latter beneath the stationary guide plate 35, thereby swinging the tongue 71 downwardly as viewed in Figure 9 so that the next container will move with dial 30 toward dial 20and will strike projection 72' to reverse the position of the deflector.

The provision of a deflector or ejector such as D to direct articles or containers in alternate directions is wellknown practice. However, if containers are moved at the relatively high linear speed discussed herein, that is,ia linear speed of the order of 1200 inches per minute it may be desirable to have the deflector operatively connected to the remainder of the mechanism :and thereby avoid its operation by the containers themselves. For example, the deflector D need not include the projections 72 and 73 but could be electrically operated under the control of a timing cam or other control device operated from or synchronized with one or both of the dials30 or 31, and which device alternately energizes solenoids to swing tongue 71' to the proper position.

In any event, by the operation under discussion, 'the dials 30 and 31 and the deflector would deliver containers alternately to the dials 20 and 21 which then would place them upon the conveyors and 11. The feed screws 22 and 23 could be used with this arrangement if it was desired to change the spacing of the containers upon the conveyors 10 and 11. It will be understood that with the Figure l arrangement used as an outfeed device, all of the elements except the conveyors 10 and 11 could be operated at a linear speed of 1200 inches per minute and the conveyors 10 and 11 could be operated at a lower linear speed, for example, half that linear speed, viz., 600 inches per minute, depending on how far apart the containers are to be spaced on the conveying elements 10 and 11. The screws 22 and 23 would decelerate containers after they have been moved clear of the dials 20 and 21. That is, the screws 22 and 23 could have their infeed (right-hand) ends at such 'pitch as to slide containers along 10 and 11 at a speed approximating that of the dials, to thereby get the containers clear of the dials before they slow to 600 inches per minute with the conveyors 10 and 11. In any event, the result would be to smoothly divide the output of the filling table or other supply mechanism and conveying element 13 between the two conveying elements 10 and '11.

Referring to the modification illustrated in Figure 8,

this illustrates two straight line conveyors or guideways.

180 and 131 which respectively direct containers or other articles to rotating disks 182 and 183 suitably journalled in a table structure 184 and having their top surfaces flush with the top surface of the adjacent conveyor elements. Assuming that the arrangement is'operated to combine containers, the parts would be operated to move containers in the direction indicated by the arrows E. By means of stationary guide elements of arcuate form generally designated 185 and 186 associated with each disk, the direction of movement of the containers is changed by 90 so that the two lines of containers now move toward each other on short straight line conveyors 186 and 187. Feed screws 183 and 189 generally similar to the feed screws 22 and 23 of Figure 1 would be provided to control the movement of the containers supplied by the conveying elements 189 and 181. As is hereinafter indicated, containers could accumulate at the infced ends of the feed screws on the disks 182 and 183 and conveying elements 180 and 181.

A fixed guide plate 190 extends between the output ends of the two screws, this plate being similar in form to the plate 35 of Figure 1 in that the container engaging edges of the plate are concentric with the axes of the two adjacent rotary dials 191 and 192 and the'apex of the guide plate extends midway between the axes of those dials. The dials 191 and 192 are provided with pockets of like number, for example, twelve, and the dials are so timed with respect to each other that their pockets move I in alignment.

The feed screws 183 and 189 are synchronized with each other so thateach screw alternately delivers a container to the adjacent dial. In other words, at the instant the dial 191 finally receives a container from the feed screw 188, the dial-189 will be initially;presenting a container to a pocket of the dial 192, with the result that when the first-mentioned container reaches a point betweenthe two dials, the container delivered'to dial .192

will be in :a position immediately following the first container. The output of the dials 191 and '192' is deand disks 182 and 183 could be operated atalinear speed of 600 inches per minute and the conveyors 186, .187 and 193 and the dials 191 and 192 could be operated at 1200 inches per minute. If each of the feed screws 188 and 189 then is operated to have an input speed of the order of 500 inches per minute and an output speed equal to the linear speed of the dials 191 and 192, and if the pitch of the outfeed end of each screw is twicethe distance between two adjacent dial pockets, containers smoothly can be combined on conveying element 193 and maintained spaced apart, just as would be the case with the first-described operation of the Figure 1 structure. It will be observed that the operation just described differs from the first operation of Figure l in that, in Figure 8, the linear speed of the outfed containers leaving the feed screws 188 and 189 will be equal to that of the conveyor elements 186 and 187, the dials 191 and 192, and the conveyor element 193.

The arrangement illustrated in Figure 8 could be operated to divide one row into a plurality of rows if the elements are driven to move containers in the direction of the arrows F. However, in such case it would be necessary to provide at the apex of guide plate 190 a deflector of the type indicated at D in Figure l or some type'such as discussed in connection with that figure. In such operation, containers spaced slightly apart and in accordance with the spacing of the pockets of the dials 191 and 192 would be delivered by the conveyor 19310 the dials 191 and 192 and deflector D will move containers alternately in opposite directions from the dials to .the conveyors 186 and .187. In this type of operation the feed screws 188 and 189 could be eliminated, though they might be designed to maintain, increase, or decrease the spacing. In any event, the net result would be'that containers moving in close relation and at high speed-on conveyor 193 could be divided into two lines whichcould travel on the conveying elements and 181 at half the speed they move on conveying element 193. Instead of-using the deflector D of Figure 1, in either that mechanism or the mechanism of Figure 8, each opposed dial such as 191 and 192 could have a cam rotatingtherewith to actuate a pusher which would eject containers from the dial pockets at the proper moment. In more detail, if the Figure 8 mechanism is operated to move containers in the direction of the arrows F, a container to move with dial 192 would be freed from dial 191 by the action of a pusher pivoted on the table structure controlled by a cam rotating with the shaft of dial 191, and containers to move with dial 191 would be freed from dial 192 by a corresponding pusher operated alternately by a cam on the shaft of dial 192.

It will be perceived that the mechanisms described above fulfill the stated objects of the invention and will enable containers or other articles to be either combined to move at an increase over their initial speed, or divided and moved at less than their infeed speed, all with a minimum possibility of the containers or other articles becoming upset, jammed or damaged.

Referring to the Figure l arrangement, and particularly when used to move containers in the direction of the arrows -A, although the use of the helical screw devices 22 and 23 results in quieter and smoother spacing of containers, nevertheless, if desired, the devices 22 and 23 may be eliminated and the line of containers on each of the conveyors 10 and 11 can be successively removedand spaced apart by the dials 2i and 21. in order to avoid jamming ofcontainers under such circumstances, the conveyors 1t and 11 would move along lines closer to the axes of the dials'22' and 23 but parallel to their travel indicated in Figure 1. In other words, the :dials 20 and 21 wouldcut-ofl? containers from the conveyors '10 and 13 11 and move each container through an arc of between 90 and 180 before the container engages the dial 30 or 31. With such arrangement, it will be clear that the dials 20 and 21 will be container-spacing control devices.

The terminology used in the specification is for the purpose of description and not of limitation, the scope of the invention being defined in the claims.

I claim: I 1

i. In a mechanism for feeding articles, a first conveyor means for a pair of lines of articles, a second conveyor means for a single line of articles, means operative to individually engage and positively control articles while on one of said conveyor means and transfer articles therefrom while maintaining individual engagement and positive control until articles are under positive control of the other conveyor means, said last-mentioned means including a pair of coacting pocketed dials, one positioned on each side of one of said conveyor means, and means to rotate said dials with their pockets in registry.

2. A mechanism of the character described in claim 1 including article deflecting means in the path of movement of articles moving from said dials.

3. A mechanism of the character described in claim 1 including article deflecting means in the path of movement of articles moving from said dials, and means to operate said deflecting means in synchronism with said dials.

4. A mechanism for feeding articles, a first conveyor means including two article-spacing control devices for separate lines of articles, each being constructed and arranged to vary the distance between centers of articles in contact therewith, a second conveyor means arranged to move articles in a single line, and means to transfer articles from one of said conveyor means to the other, said transfer means being constructed and arranged to individually engage and positively control articles traveling on one of said conveyor means and to maintain individual engagement and positive control of the articles until transferred onto and under positive control of the other of said conveyor means.

5. A mechanism of the character described in claim 4 wherein said second conveyor means includes a straight line conveyor element and a third article-spacing control device positioned alongside thereof. I

6. A mechanism of the character described in claim 4 wherein said second conveyor means comprises a straight line conveyor movable between fixed guides.

7. A mechanism of the character described in claim 4 wherein said article spacing control devices are operated to move articles at a slower linear speed than that of articles moving with said second conveyor means.

8. A mechanism of the character described in claim 4 wherein said transfer means includes a pair of pocketed dials positioned on opposite sides of said second conveyor means and having their pockets spaced circumferentially by a distance corresponding to the distance between centers of articles on said second conveyor means.

9. A mechanism of the character described in claim 8 including means to drive said pocketed dials with their pockets in registry.

10. In a mechanism for feeding articles, a first conveyor means including two article conveying elements and a pair of article-spacing control devices, one along the path of travel of each of said conveying elements, a second conveyor means including a single article conveying element, and means to transfer articlesbetween said second conveying means and alternately with respect to the'two article conveying elements of said first conveyor means.

11. A mechanism of the character described in claim 10 wherein said article-spacing control devices each include a substantially cylindrical helically threaded element having an axis of rotation substantially parallel to said two article-conveying elements.

12. A mechanism of the character described in claim l0 wherein said article'spacing control devices are constructed and arranged to change the spacing between the articles moving in contact therewith.

13. A mechanism of the character described in claim 10 wherein said article-spacing control devices are con structed and arranged to change the spacing between articles moving in contact therewith, and an article-spacing control device is positioned along the path of travel of the article conveying element of said second conveyor means, said last-mentioned device being constructed and arranged to maintain articles moving in contact therewith spaced on fixed centers.

14. A mechanism of the character described in claim 10 wherein said means to transfer articles from one conveyor means to the other includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means.

15. A mechanism of the character described in claim 10 wherein said means to transfer articles from one conveyor means to the other includes a first pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and a second pair of rotary members interposed between said dials and the respective article conveying elements of said first conveyor means.

16. A mechanism of the character described in claim 10 wherein said article-spacing control devices are operated out of phase with each other.

17. A mechanism of the character described in claim 10 wherein said means to transfer articles from one conveyor means to the other includes a first pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and a second pair of rotary pocketed dials interposed between said first first dials and the respective article conveying elements of said first conveyor means, each of the dials of said first pair being provided with a number of pockets which is a multiple of the number of pockets provided in each of the dials of said second pair.

18. A mechanism of the character described in claim 17 wherein all of said dials are formed to move articles on circular paths of like radius.

19. A mechanism of the character described in claim 17 wherein all of said dials are formed to move articles on circular paths of like radius, said first and second conveyor means are positioned on opposite sides of said dials with their article conveying elements parallel, and the article conveying elements of said first conveyor means are laterally displaced in opposite directions from the article conveying element of said second conveyor means.

20. In a mechanism for feeding articles, a first conveyor means including two article conveying elements and a pair of article-spacing control devices, one along the path of travel of each of said conveying elements, a second conveyor means including a single article conveying element, and means to transfer and combine articles alternately by individually engaging and positively controlling the articles from the article conveying elements of said first conveyor means until the articles are combined on the article conveying element of said second conveyor means.

21. A mechanism of the character described in claim 20 wherein said article-spacing control devices are helical screw members having aXes of rotation substantially parallel to the direction along which articles move.

22. A mechanism of the character described in claim 20 wherein said article-spacing control devices are operated out of phase with each other.

23. A mechanism of the character described in claim 20 wherein said means to transfer articles from the conticle conveying element of said second conveyor means includes a pair of rotary pocketed dials positioned between the outfeed end of said first conveyor means and the infeed end of said second conveyor means, said dials being positioned on opposite sides of the article conveying element of said second conveyor means.

24. A mechanism of the character described in claim 20 wherein said article-spacing control devices are helical screw members of gradually increasing pitch in the direction along which the articles move.

25. A mechanism of the character described in claim 20 wherein said article-spacing control devices are helical screw members of gradually increasing pitch in the direction along which the articles move, and an articlespacing control device is positioned along the path of travel of the article conveying element of said second conveyor means, said last-mentioned means being constructed and arranged to maintainarticles moving in contact therewith spaced on fixed centers.

26. A mechanism of the character described in claim 20 wherein said means to transfer articles alternately from the article conveying elements of said first conveyor means to the article conveying element of said'second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means.

27. A mechanism of the character described in claim 20 wherein said means to transfer articles alternately from the article conveying elements vof said first conveyor means to the article conveying element of said second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and means to rotate said dials with their pockets in synchronism.

28. A mechanism of the character described in claim 20 wherein said means totransfer articles from the conveying elements of said first conveyor means to the article conveying element of said second conveyor means includes a pair of rotary pocketed dials positioned between the outfeed end of said first conveyor means .and the infeed end of said second conveyor means, said dials being positioned on opposite sides of the article conveying element of said second conveyor'means, and said article-spacing control devices operate to outfeed articles at a linear speed less than that of said dials.

29. A mechanism of the character described in claim 28 wherein all of said conveying elements and said dials move at the same linear speed.

30. A mechanism of the character described in claim 20 wherein said means to transfer articles alternately from the article conveying elements of said first conveyor means to the article conveying element of said second conveyor means includes a'first pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and a second pair of rotary pocketed dials interposed between said first dials and the respective article conveying elements of said first conveyor means, each of the dials of said first pair being provided with a number of pockets which is a multiple of the number of pockets provided inv each of the dials of said second pair.

31. A mechanism of the character described in claim 30 wherein all of said dials are formed to move articles on circular paths of like radius.

32. A mechanism of the character described in claim 30 wherein all of said dials are formed to move articles on circular paths of like radius, the article conveying elements of saidfirst "conveyor means being arranged to deliver articles to the respective dials of said second pair of dials, andthe respective dials of said first pair of dials being adapted to simultaneously engage articles alternately delivered thereto by said second dials and-deliver the 7 articles to said second conveyor means.

33. In a mechanism for feeding articles, a first con 16 veyor .means including two article conveying elements and apair of article-spacing control devices, one along the path of travel of each of said conveying elements, a second conveyor means including a single article conveying element, and means to transfer articles alternately from the article conveying element of said second conveyor means to the article conveying elements of said first conveyor means.

34. A mechanism of the character described in claim 33 wherein said article-spacing control devices are constructed and arranged to decrease the spacing between articles moving in contact therewith.

35. A mechanism of the character described in claim 33 wherein said means to transfer articles from said second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means.

36. A mechanism of the character described in claim 33 wherein said means to transfer articles from said second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and means to drive said dials with their pockets in synchronism.

37. A mechanism of the character described in claim 33 wherein said means to transfer articles from said second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conveyor means, and a pair of rotary members interposed between said dials and the respective article conveying elements of said first conveyor means.

38. A mechanism of the character described in claim 33 wherein said transfer means includes an article defiecting member operable in synchronism with said second conveyor means.

39. A mechanism of the character described in claim 33 wherein said means to transfer articles from said second conveyor means includes a pair of rotary pocketed dials positioned between said first and second conveyor means, one at each side of said second conve'or means, and a second pair of rotary pocketed dials interposed between said first dials and the respective article conveying elements of said first conveyor means, each of the dials of said first pair being provided with a number of pockets which is a multiple of the number of pockets provided in each of the dials of said second pair.

40. A mechanism of the character described in claim 39 wherein all of said dials are formed to move articles on circular paths of like radius.

41. A mechanism of the character described in claim 39 wherein all of said dials are formed to move articles on circular paths of like radius, said first and second conveyor means being positioned on opposite sides of said dials with their article conveying elements parallel, and the article conveying elements of said first conveyor means are laterally displaced in opposite directions from the article conveying element of said second conveyor means.

42. A mechanism of the character described in claim 39 wherein all of said dials are formed to move articles on circular paths of like radius, said first and second conveyor means are positioned on opposite sides of said dials with their article conveying elements parallel, and the article conveying elements of said first conveyor means and said second dials being on opposite sides of the article conveying element of said second conveyor means and said first dials.

43. In a mechanism for feeding articles; first and second article supporting and delivery conveying elements, a third article supporting and conveying element positioned to receive articles from said first and second elements, three helically threaded elements, one positioned alongside each of said three article supporting and conveying elements to control the spacing of articles moving therewith, means to drive said helical elements in synchronism with each other, and means cooperating with said helical elements to guide articles from said first and second elements to said third element.

44. A mechanism of the character described in claim 43 wherein said third supporting and conveying element is positioned between and substantially parallel to said first and second supporting and delivery conveying elements.

45. A mechanism of the character described in claim 43 wherein said means cooperating with said helical elements is effective to alternately guide articles from said first and second elements to said third element.

46. A mechanism of the character described in claim 43 including means to rotate said helical elements positioned alongside said first and second article supporting and delivery conveying elements symmetrically out of phase with each other.

47. In a mechanism of the character described, a cylindrical helically threaded element, a plurality of articlemoving means in transfer relation with said element, each of said article-moving means having transfer points respectively coinciding with adjacent spirals on the same side of said helical element, said article-moving means including means to positively engage and control articles while articles are traveling on said article-moving means and until articles are transferred to and under positive control of said helical element, and means to operate said helical element and each of said article-moving means in timed relation.

48. Mechanism of the character described in claim 47 wherein each of said article moving means includes a helically threaded element and said last-named elements are out of phase with each other.

References Cited in the file of this patent UNITED STATES PATENTS 1,828,324 Kruse Oct. 20, 1931 2,108,522 Bergmann Feb. 15, 1938 2,156,105 Bergmann Apr. 25, 1939 2,202,033 Steward et al. May 28, 1940 2,266,497 Huntley et al. Dec. 16, 1941 2,335,239 Gladfelter et al. Nov. 30, 1943 2,371,419 Bergmann Mar. 13, 1945 2,535,859 McPherson Dec. 26, 1950 2,563,496 Schmidt Aug. 7, 1951 2,620,058 Smith et al. Dec. 2, 1952 2,630,904 Bozek Mar. 10, 1953 2,645,399 Bozek July 14, 1953 2,663,401 Dascomb Dec. 22, 1953 2,692,671 Day Oct. 26, 1954 2,750,722 Ferguson June 19, 1956

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