Oscillating head filler device

An arrangement for use in a conveying and filling device where a conveyor is provided which travels along a linear path in a selected direction to carry articles, for example, recepticles to be filled. A dispensing device is carried by a mounting arm located in spaced relation from the conveyor and is carried by crank means to travel in an orbital path where the orbit carries the mounting arm in the direction of movement of the conveyor for the first portion of the orbit at the termination of which the orbital path returns the mounting arm to a second position relative to the conveyor for a second cycle over the conveyor, including a height adjusting arrangement to adjust the clearance between the mounting arm and the conveyor.

BACKGROUND OF THE INVENTION 
The present invention relates to a device for adjusting the clearance 
between a mounting arm traveling in an orbital path above a moving 
conveyor and the conveyor is particularly useful in applications where the 
mounting arm carries a dispensing device to a fill containers carried by 
the conveyor. 
In operation of such devices the adjustment between the clearance between 
the mounting arm, the associated dispensing device and the top of the 
conveyor is critical in that it affects the area over which the material 
is dispensed and the dispensing pattern. 
In other applications the clearance may be critical to avoid fluid 
splashing out of the containers and loss of the material from the 
container. Such an occurance is particularly undesirable where in a 
subsequent operation a lid is applied to the container, for example, by 
gluing or heat sealing to a flange provided around the periphery of the 
container and the presence of the material on the lip or flange impairs 
sealing. 
Various prior art arrangements are available for moving a dispensing device 
with a moving conveyor where containers are carried by the conveyor, 
however, in known prior art arrangements the clearance adjustment is 
accomplished manually and requires termination of the operation of the 
device for adjustment of the clearance. 
No prior art arrangement is known providing means for the adjusting the 
clearance between the dispensing device and articles carried on the 
conveying line during operation by adjusting the position of a mounting 
arm which carries a dispensing head. Prior art devices are known where the 
dispensing head is carried by a servo mechanism carried by the mounting 
arm but such arrangements are first of all expensive to build and are 
generally not reliable over an extended period of time so further expense 
is incurred in lost production time for repair and for maintenance 
expense. 
The ability to adjust the height of a dispensing device above a conveyor is 
advantageous particularly when the material being dispensed is a liquid 
where the viscousity of the liquid may vary with time as a result of 
changes in temperature or changes in composition so that the area over 
which the material is disposed or the pattern is changed and the clearance 
between the dispensing device and the recepticals must be frequently 
adjusted. 
SUMMARY OF THE INVENTION 
The present invention provides a straightforward, economical arrangement 
for adjusting the clearance between a mounting arm which can carry a 
dispensing device, and a conveying line where the mounting arm travels in 
an orbital path about an axis perpendicular to, and in spaced relation 
from the axis of travel of the conveying line whereby a first portion of 
the orbit the mounting arm travels with the conveyor from a first 
position, then returns to travel with the conveyor in a subsequent cycle. 
The present invention provides for adjustment of the clearance between the 
mounting arm, and the conveyor during operation of the device. 
Various prior art arrangements are known where the adjustment of the 
clearance is accomplished by shutting the line down and manually adjusting 
the height of the mounting arm, however, such arrangements have been found 
to be particularly cumbersome, expensive, and undesirable because of lost 
time in shutting down the line for height adjustment and where several 
attempts may be necessary to obtain proper adjustment because of the 
inability to ascertain the effects of the change while the unit is not in 
operation. 
More particularly, the present invention provides an arrangement for use in 
a conveying and filling device where a conveyor is provided which travels 
along a linear path in a selected direction to carry articles, for 
example, recepticles to be filled. A dispensing device is carried by a 
mounting arm located in spaced relation from the conveyor and is carried 
by crank means to travel in an orbital path where the orbit carries the 
mounting arm in the direction of movement of the conveyor for the first 
portion of the orbit at the termination of which the orbital path returns 
the mounting arm to a second position relative to the conveyor for a 
second cycle over the conveyor, including a height adjusting arrangement 
to adjust the clearance between the mounting arm and the conveyor. 
While one example in accordance with the present invention is illustrated 
in connection with the accompanying drawings, it will be recognized that 
other arrangements, also within the scope of the present invention, will 
occur to those skilled in the art upon reading the disclosure set forth 
hereinafter.

DETAILED DESCRIPTION OF THE DRAWINGS 
Referring first to FIG. 1 which illustrates a perspective view of the front 
side of a unit within the scope of the present invention, a moving 
conveyor 1 is shown having multiple sections, each including apertures 2 
for receipt of, for example, a container to carry a food product. Conveyor 
1 moves in a direction illustrated by arrow A at a uniform velocity. 
Likewise conveyor 1 is carried by a frame 3 and driven by motive means 
(not shown) and has a return leg 1A. A drive shaft 6, driven by a power 
source, (not shown) is provided to drive the device within the scope of 
the present invention as described hereinafter. Drive shaft 6 can be 
driven by the same motive means as the conveyor so that the conveyor and 
device within the scope of the present invention are driven at fixed 
relative rates of speed. A sprocket 5 is provided on shaft 6 to drive, for 
example, and endless chain 4. Referring to FIG. 2 a drive means 34, for 
example, a right angle gear box 32 is the dynamic differential provided 
including an input sprocket 42 driven by chain 4. 
A frame 7 is provided having cross members 8, 9 and 15 with spaced cross 
members 8A, 9A, 15A which are carried by brackets 10, 10A, 25, 25A, 30, 
30A as shown in FIG. 2 and adapted to receive the mechanism described 
hereinafter, therebetween to adjust the position of a mounting arm 16 
above conveyor 1. 
As described hereinafter in more detail, mounting arm 16 moves in orbital 
path having an axis transverse to and in spaced relation above the path 
traveled by conveyor 1. Advantageously, in the first portion of the orbit 
where the mounting arm is closest to conveyor 1 the mounting arm moves 
with the conveyor 1 in the direction illustrated by the arrow A (FIG. 1) 
and for a portion of the time moves at a speed nearly equivalent to the 
velocity of conveyor 1. 
In one arrangement the speed of arm 16 approximates the speed of conveyor 1 
when arm 16 is at the bottom of its orbit. 
In this arrangement, arm 16 does not move significantly faster than 
conveyor 1 even at the bottom of the orbit. 
In another arrangement the drive elements are selected so that the linear 
components of the speed of arm 16 parallel to conveyor 1 is equal to the 
speed of conveyor 1 just before and just after bottom center where the arm 
16 is closest to conveyor 1 and the linear speed component is selectively 
greater than the speed of conveyor 1. 
It has been found that in this manner, the effective dwell line of arm 16 
can be increased particularly where arm 16, for example, initially aligns 
itself with a position selectively near the rear edge of a container on 
conveyor 1 then moves from the rear of the container to near the front of 
the container as arm 16 moves faster than conveyor 1 and finally reduces 
speed to equal the speed of conveyor 1 as the arm approaches the front end 
of the conveyor. 
The mounting arm then returns through a second portion of the orbit to the 
point where the first portion again commences. 
As shown, a hand wheel 23 is provided connected for rotation of a shaft 24 
as described hereinafter for adjustment of the clearance between mounting 
arm 16 and the top of conveyor 1. As further shown in FIG. 1 mounting arm 
16 can be adapted to carry dispensers 16A, only one being shown, but it 
being understood that multiple dispensers are usually provided and 
depending upon the speed of rotation of mounting arm 16 two or more 
distributors in line may be provided. In the example shown, three 
dispensers across would be provided to adequately serve the containers 
provided in each of the apertures 2. Mounting arm 16 is carried within 
guide members 17 for vertical adjustment therebetween. As hereinafter 
described, the height of mounting arm 16 is adjustable relative to 
conveyor 1 by means of rotation of a threaded shaft 14 which is received 
in a threaded fitting carried by mounting arm 16 (not shown) so that 
mounting arm 16 is raised and lowered depending on the direction of 
rotation of shaft 14. A coupling 13 is provided to connect shaft 14 to a 
right angle angle drive 12, which is carried by an oscillating arm 11 as 
are guides 17 which carry mounting arm 16 which moves with arm 11. 
Referring to FIGS. 1, 2 and 3, in relevant position which illustrate the 
location and configuration of elements which make up and drive the 
oscillating arm 11, arm 11 is provided with journals 20A and 20B to 
receive pivots 20 and 22 carried eccentrically by crank wheels 22A, 22B 
rotated at the same rate of travel by shafts 26, 27. Arm 11 travels in an 
orbital path by rotation of wheel 23 and shaft 24 which are cooperatively 
positioned for such movement and carries mounting arm 16 in an orbital 
path above conveyor 1 and the direction of travel of conveyor 1 for a 
first portion of the orbit that dispenser 16A can be actuated to deposit 
fluid on recepticles carried in operations. Actuation of dispensers 16A 
can be accomplished by various means known in the art. In one arrangement 
(not shown) the dispensers are actuated during a selected portion of the 
orbital path of arm 11 and usually during the portion of the orbit when 
arm 11 is at the lowest position. 
As shown in FIG. 1 horizontal cross member 8 is provided to journal shaft 
26 and shaft 27 is journaled in cross member 15. A drive means, for 
example a sprocket 18, as shown in FIGS. 1, 2 and 3 is provided by drive 
34 for rotation of an endless chain 18A, as described hereinafter. Chain 
18 drives a sprocket 41, as shown, which drives shaft 27 and crank 22B. A 
sprocket 46 is provided on shaft 27 and connected to drive a sprocket 47 
carried by shaft 26 by means of an endless chain 19 to assure uniform 
rotation of cranks 22A and 22B. 
Counterweights 49 and 58 are provided to be carried by shafts 26 and 27 to 
offset the weight of mounting arm 16 and any appurtenances as best shown 
in FIGS. 2 and 3. 
Accordingly, rotation of shaft 27, at a speed determined by the speed of 
rotation of shaft 6, the configuration of drive 34 and the relative sizes 
of the chain sprockets determine the orbital speed of arm 16 where it is 
desirable that the speed in the first portion of the orbit be generally 
equal to the speed of conveyor 1. 
As shown, gearbox 34 is provided with a second output sprocket 62 to drive 
a chain 36 where a tensioning device 36A is provided to maintain the 
tension of chain 36 where chain 36 drives one input sprocket 37 of a 
planetary differential gear drive 32 described hereinafter having a second 
input shaft 33 connected through an angle gear drive 31 to shaft 24 which 
is rotated by wheel 23 as previously described. An output shaft 69 (shown 
in FIG. 3) is provided to drive a sprocket 70 and chain 71 as shown. 
Chain 71 drives a sprocket 73 carried by a shaft 74 where sprocket 73 
carries a gear wheel 76. A second gear wheel 77 is provided to mate with 
gear wheel 76 and is carried by an shaft 80 of angle drive 12. 
Planetary differential 32 can, for example be of the type manufactured by 
Hart Design & Manufacturing Co. Inc. of Green Bay Wis. Such a device has a 
first input shaft 33, a second input sprocket 37 and an output shaft 69 to 
drive sprocket 70. As is known in the art, the internal construction (not 
shown) of such a device generally consists of helical gear planatary 
means. Ordinarily one shaft extension transmission is secured to the 
spider of the the helical gear plantary. Pinions or planets mounted on 
ball bearings located in the spidering engage one sun gear referred to as 
the output gear where the output gear is secured to a shaft which is part 
of the second shaft extension. A normally stationary sun gear referred to 
as the held gear is located such that the second set of pinions or planets 
are engaged with the held gear. Because the held gear is secured to the 
worm gear in normal operation, neither will rotate but will be held in 
fixed position due to the engagement of the worm gear with the worm. In 
this case the worm is secured to the shaft 33 and prevents creep or 
accidental rotation of the handwheel shaft. The planetary gears can be 
selected with the proper number of teeth to provide a one to one direction 
of rotation with respect to the direction of rotation of the shaft. That 
is exactly one revolution of the input shaft in one direction will result 
in exactly one revolution of the output shaft in the opposite direction or 
a negative direction of rotation. However rotation of the shaft in the 
opposite direction will result in a positive direction of rotation. In one 
example of a planetary differential as used in the present invention, the 
worm gear is selected such that one revolution of the hand gear will 
result in for example, 12.degree. rotation of the output shaft with 
respect to the input shaft where the extent of rotation of the output 
shaft is the sum of the rotation of the rotating input shaft, in this case 
driven by sprocket 37 and the adjustment shaft. Thus in operation sprocket 
37 is rotated by chain 36 from gearbox 34 (FIG. 2) which is drawn from 
conveyor drive shaft 6 as previously described. Without adjustment of 
shaft 35, sprocket 70 rotates at a given rate. However adjustment of shaft 
35 causes an arcuate advance or retreat of sprocket 70 relative to the 
rotation of sprocket 37 and directly affects the position of gear wheel 72 
on gear wheel 76 as described hereinafter. 
As can be seen from the drawings, gear wheel 77 is carried by rotatable 
shaft 80 which provides the input for right angle gear 12. Shaft 74 is 
journaled in cross members 9, 9A and the centerline spacing between shafts 
74 and 80 is selected to allow continuous mesh of gear wheels 76 and 77. 
Further, speed of rotation and sprocket sizes and sizes of gear wheels 76, 
77 are selected so that as arm 11 orbits as result of cooperative rotation 
of cranks 23, 24 gear 77 orbits around gear wheel 76 at the same speed as 
the speed of rotation of gear 76 when there is no adjustment of wheel 23 
so there is no rotation of shaft 80. As previously described shaft 80 by 
means of angle drive 12 causes rotation of threaded shaft 14 which raises 
or lowers mounting arm 16 depending on the direction of rotation of shaft 
80. Shaft 80 is rotated when the arc through which gear wheel 76 rotates 
is different than the arc through which orbiting gear wheel 77 passes. The 
difference occurs as previously described, when shaft 24 is turned to 
introduce an incremental change in the arc of rotation of output shaft 69 
apart from the arc of rotation normally provided by rotation of input 
sprocket 37. 
Since the speed of rotation of sprocket 37 is proportional to the speed of 
shaft 6 and the speed of rotation of cranks 23 and 24 is likewise 
determined by the speed of shaft 6, the interconnecting drive trains are 
selected so that gear wheel 77 orbits gear wheel 76 so that shaft 80 does 
not rotate except when shaft 24 is adjusted. The arcuate travel of gear 
wheel 76 is adjusted and rotates gear wheel 77 as described hereinafter. 
Further in accordance with the present invention, it will be understood 
that while the principal drive for the device described hereinbefore and 
hereinafter is from the drive shaft of the conveyor, other drive means 
could be provided, it only being necessary that synchronization and 
indexing of the various elements of the device be maintained by means of 
proper selection of, inter alia, speed, sprocket diameters and gear 
transmission ratios. 
In operation, with conveyor 1 running, drive chain 4 rotates sprocket 42 to 
provide input drive to gearbox 34. Output sprocket 18 rotates chain 18A 
which in turn rotates sprocket 41 and shaft 27 thereby rotating sprockets 
46, 47 (by means of chain 48) and cranks 22A, 23A at the selected speed to 
provide the orbital motion of arm 11 and mounting arm 16. As previously 
described counterweights 49 and 50 are provided on shafts 26 and 27 to 
balance the weight of the mounting arm 16 and its associated elements 
including various dispensers 16A which may be carried thereby. 
Sprocket 62 of gear box 34 drives differential 32 by means of chain 36. An 
output sprocket 70 is provided from planetary differential 32 to drive 
chain 71. 
As previously described, the rotation of chain 71 is determined by the 
speed of rotation of sprocket 70 and the rotation, if any, of shaft 24 
where the rotation is transmitted through angle gear box 31 and shaft 33. 
So long as there is no rotation of shaft 24 then advantageously chain 71 
rotates at a speed sufficient to provide no rotation of shaft 80 because 
gear wheel 77 orbits around gear wheel 76 at the speed of rotation of 
wheel 76, so the contact point between gear wheels 76 and 77 remains 
static until rotation of shaft 24 as described hereinafter. 
FIGS. 4A-4D are schematic illustrations of the operation of the adjusting 
means utilized in adjusting the height of mounting arm 16 above conveyor 
1. 
More particularly, in FIG. 4A cranks 23-24 are shown with arm 11 connected 
therebetween. It will be understood from the previous discussion that 
cranks 22A and 22B are rotated by means of shafts 26 and 27 where arm 11 
is connected at opposite ends to cranks 22A and 22B by pivots 20 and 22 
respectively. 
In FIG. 4A the device is shown with the cranks 22A, 22B in a position where 
pivots 20 and 22 are in aligned relation along a center line 90. It will 
be noted for reference purposes the contact point between gear wheels 77 
and 76 is noted by the reference numeral B. At the position shown in FIG. 
4A chain 71 has a relative reference point 91 (the position of a selected 
point of chain 71). Likewise a reference point 98 is shown on conveyor 1. 
In FIG. 4B cranks 22A, 22B have turned through a one quarter revolution so 
that gear wheel 77 is shown in the clockwise 90.degree. position where it 
will be noted that the gear wheel 76 and 77 are still in contact at 
reference B. Chain 71 has moved from reference point 91 to reference point 
92 and conveyor 1 has moved from reference point 98 to reference point 99. 
In FIG. 4C cranks 22A and 22B have rotated through an additional 90.degree. 
arc in a clockwise direction and once again are in aligned relation on 
centerline 90 but with arm 16 at the low point of the orbit. Chain 71 has 
progressed from position 92 to position 93 rotating wheel 76 a like amount 
where gear wheel 77 has likewise rotated through 90.degree. so wheels 76 
and 77 are still in contact at point B. Likewise conveyor 1 has progressed 
to reference point 100. 
FIG. 4D illustrates the effect of rotation of shaft 24 while the 
arrangement is in the position shown in FIG. 4C. In FIG. 4D shaft 24 (not 
shown) has been rotated an amount sufficient to rotate wheel 76 through an 
arc D so that wheel 77 and shaft 80 are likewise rotated through an arc D 
and the previous contact point B has now been rotated to point B'. In 
connection with previous described it has been disclosed that rotation of 
shaft 80, carried by gear wheel 77, connected through right angle drive 12 
causes rotation of shaft 14 which raises or lowers arm 16. Accordingly, as 
shown in FIG. 4D the rotation of gear wheel 76 through the additional arc 
D has rotated shaft 14 to lower the bottom of arm 16 from point F to point 
G through a distance E. 
It will be understood that rotation of shaft 24 in the opposite direction 
would raise arm 16. It will be understood that the adjustment described 
with reference to FIGS. 4C and 4D can be made while the previously 
described device is rotating. 
It will be understood that the foregoing is but one example of an 
arrangement and application of devices within the scope of the present 
invention and that various other arrangements and applications will 
likewise occur to those skilled in the art upon reading the disclosure set 
forth hereinbefore.