Seal roll index

An apparatus for indexing a seal roll which is engagable by a heat seal head to prevent the contact area of said heat seal head from successive landing at the same location on the seal roll includes a driven pulley mounted coaxially with the seal roll and components for indexing to turn the driven pulley. The components include a rocker mounted on a common axis with a drive pulley via a one-way clutch and an actuator connected eccentrically to the rocker such that reciprocating motion of the actuator rotates the rocker in opposite directions. In one direction, the rocker rotates the drive pulley via the one-way clutch to index the roll via the drive belt and driven pulley. In an opposite direction, the clutch permits rotation of the rocker in the opposite direction free of rotation of the drive pulley. A brake member is connected to the rocker eccentrically of the common axis, the brake member clamping the drive belt against a stop member for seizing rotation of the roll during the heat seal procedure.

FIELD OF THE INVENTION 
The present invention relates to heat sealing equipment, and particularly 
to heat sealing equipment for sealing tube stock to form bags, including a 
dual acting air cylinder which effects braking and indexing of a seal roll 
operatively associated with a reciprocating heat seal head. 
BACKGROUND OF THE INVENTION 
Plastic bags can be formed, or sealed by transporting an elongate web of 
bag stock through a heat sealing station and intermittently sealing the 
tubular stock across a width thereof. The heat sealing station includes a 
reciprocating heat seal head which is brought into pressing contact with 
the tubular stock supported on a seal roll. It is known to intermittently 
rotate the seal roll to provide a cooled landing surface area on the seal 
roll for the heat seal head for heat sealing each intermittent heat seal 
region across the width of the tubular stock. 
According to present technology, a main servo-drive rotates coacting draw 
rolls to translate tube stock through a heat seal station, including the 
heat seal head and cooperating seal roll, which main servo drive also 
drives a gear train to drive the seal roll. The gear train is a 
maintenance concern and the additional load on the main servo-drive limits 
the speed of the servo drive. Also, backlash in the gear train can 
adversely affect the quality of the heat seals. The backlash allows the 
seal roll to float when the seal head comes into contact therewith. 
Also known is an indexing device which uses an overrunning clutch on the 
seal roll. The device uses two bands tensioned with springs, one for 
indexing and one for braking. The braking mechanism is always engaged and 
is overcome by the indexing band. An oscillating shaft is used to provide 
the linear motion to pull on the indexing band to rotate the seal roll. 
A similar device is known which relocates the overrunning clutch from the 
seal roll to mount to an intermediate shaft that is geared to the seal 
roll. Also known is the use of a cam instead of the oscillating shaft to 
provide the linear motion to pull on the indexing band and to rotate the 
seal roll. 
SUMMARY OF THE INVENTION 
The present invention provides a dual-acting, air cylinder to be used as a 
power source to rotate, stop and then hold a seal roll in position during 
a sealing operation. The linear movement of the air cylinder is converted 
into rotary motion with the use of a rocker. This rocker is connected to a 
drive pulley through an overrunning clutch and bearing. The drive pulley 
rotates the seal roll with a flexible drive belt. The overrunning clutch 
allows the rocker to rotate the drive pulley in only a first direction. 
When the rocker is rotated in a second direction, the rocker is used to 
brake the belt. 
The device of the present invention has two modes of operation: braking and 
indexing. In the braking mode of operation, positive air pressure is 
supplied to one side of an air cylinder while the other side is open to 
the atmosphere, causing a piston within the air cylinder to move to 
retract an output shaft. When the piston is retracted, the flexible drive 
belt is pinched between the rocker and a stop. When the belt is pinched, 
i.e., the brake is actuated, the belt and the seal roll are positively 
stopped and restrained from any movement. 
After a sealing operation is completed and a signal is given to index, the 
air pressure inputs to the cylinder are reversed, causing the piston 
within the air cylinder to extend the output shaft and the rocker to 
rotate in the first direction. The rotation of the rocker simultaneously 
releases the brake and rotates the drive pulley in the first direction via 
the overrunning clutch. Consequently, the drive pulley rotates the seal 
roll via the flexible belt. Since the drive pulley is mounted on the 
overrunning clutch, the seal roll and drive pulley are free to rotate in 
the direction of the index. In order to stop the seal roll from 
overrunning after an index, the brake is reapplied by reversing the air 
pressure to the cylinder and rotating the rocker in the second direction. 
The brake remains engaged through the sealing cycle until a signal is 
given for another index movement. The amount of movement of the index is 
determined by the amount of the time that the air pressure is switched. 
Holding the seal roll stationary during heat sealing by use of the brake 
allows for a more precise and effective heat seal compared to prior art 
apparatus which allow some movement of the seal roll during heat sealing. 
The seal roll index apparatus of the present invention effectively 
separates the seal roll index driving mechanism from the main servo drive. 
Thus the problems associated with driving the heat seal roll index using a 
gear train driven by the main servo drive is eliminated by the independent 
seal roll index drive of the present invention. 
Other features and advantages of the present invention will become readily 
apparent from the following detailed description of the accompanying 
drawings, and the appended claims.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
While the present invention is susceptible of embodiment in various forms, 
there is shown in the drawings and will hereinafter be described presently 
preferred embodiments with the understanding that the present disclosure 
is to be considered an exemplification of the invention and is not 
intended to limit the invention to the specific embodiments illustrated. 
FIG. 1 illustrates a bag sealing apparatus 10 of the present invention. The 
sealing apparatus includes a heat sealing mechanism 12 having a heat 
sealing head 14 in opposition to a seal roll 16. The head is heated and 
composed of metal, the seal roll is composed of rubber coated steel and 
covered with Teflon tape. 
Once folded, plastic bag stock 20, having a folded longitudinal edge and an 
open longitudinal edge and arranged in a folded flat configuration, is 
progressed through the heat sealing region 22 by draw rollers 30, 32 of a 
servo drive. The draw rollers 30, 32 are located close to and upstream of 
the heat seal region 22. The heat sealing mechanism 12 is reciprocatable 
along the direction Y downwardly to cause the heat sealing head 14 to 
press the bag stock 20 to the seal roll 16 to effect a heat seal 36 across 
the width of the bag stock 20 and intermittently along the length of the 
bag stock 20; and upwardly to allow the bag stock to be moved by the 
roller 30, 32 along the direction X. 
The heat seals 36 close lateral edges of individual bags 37 which are 
separated by the action of the heat seal head 14 from the bag stock 20. 
Thus each bag 37 is closed on three sides by a lengthwise fold of the bag 
stock 20 (not shown) and two heat seals 36. 
A rotating wicketer 38 receives the bags 37 successively from the heat seal 
region 22 on revolving arms 39 which hold the bags 37 by vacuum and 
deliver the bags 37 to a further station or conveyor (not shown). 
A rocker 40 is provided pivoted about a center axis 42. The rocker 40 in 
FIG. 1 is shaped in the form of a segment of a circle. The rocker 40 
pivots about a pivot connection 44 to a pneumatic linear positioner 45 
including an air cylinder actuator 46. The actuator includes an extendable 
shaft 48 connected to a round lug 50 at the pivot connection 44. The 
actuator 46 is pin-connected at a top lug 52 to stationary support 
structure 56. 
At an opposite end of the rocker 40 from the pivot connection 44 is a brake 
roller 58 pinned to the rocker 40. A drive pulley 60 is mounted flushly to 
the rocker 40 and having the same axis of rotation 42. Mounted at an axial 
end of the seal roll 16 is a driven roll pulley 62. The roll pulley 62 is 
fixed for rotation with the seal roll 16 about an axis 64. A drive belt 66 
is wound around the drive pulley 60 and the roll pulley 62. Hence, 
forcible rotation of the drive pulley 60 causes a corresponding rotation 
of the roll pulley 62. 
The belt can be a standard neoprene backed belt, or a polyurethane belt if 
belt wear is excessive. 
The actuator 46 includes a tubular pneumatic cylinder 70 having a first 
pneumatic port 72 connected to a first port 73 of a four-way pneumatic 
valve 74 having an air supply inlet 76, tube connected to compressed air 
80, and an air bleed to atmosphere 78 through a muffler 79. A second 
pneumatic port 90 into the cylinder 70 is tube connected to a second port 
91 of the four-way valve 74. Compressed air 80 can thus be supplied into 
the cylinder 70 depending on a control signal 82 from a controller 84. In 
the configuration illustrated the signal 82 is a zero signal, or no 
signal. The controller 84 can be an electronic controller or can simply be 
a synchronized signal from a timer, roller, gear or other repeated 
synchronized signal. 
The four-way valve is urged by a spring 92 to the configuration shown in 
FIG. 1. The valve 74 includes a first valve block 95 having straight 
through channels 95a, 95b, and a second valve block 96 having crossed 
channels 96a, 96b. The valve has a solenoid actuator 97 which when 
activated moves the blocks 95, 96 toward the spring 92, to compress the 
spring, and assume the configuration shown in FIG. 2. 
In the configuration shown in FIG. 1, the ports 73, 91 are connected to 
channels 95a, 95b which are connected to the muffler 79 and air supply 
inlet 76 respectively. When changed to the configuration of FIG. 2, the 
port 73 is connected to the air supply inlet 76 through the cross channel 
96b and the port 91 is connected to the muffler 79 through the cross 
channel 96a. To switch from the configuration of the valve 74 illustrated 
in FIG. 1 to that shown in FIG. 2 a signal 98 is sent from the controller 
84 to the solenoid actuator 97. 
Adjacent the brake roller 58 is a stop 110 which is located on an outside 
of the belt 66 in close proximity thereto. The stop 110 can be a 
stationary abutment or a roller. 
When the rocker 40 is pivoted an angular amount in a counterclockwise 
direction by movement of the shaft 48 in the direction Y2, the brake 
roller 58 squeezes the belt 66 against the stop 110 to cause an immediate 
braking of the belt 66. In the position shown in FIG. 1, the belt 66 is 
braked and the heat seal tool 12 has been lowered in the direction Y so 
that the seal head 14 has pressed the bag stock 20 downwardly onto the 
seal roll 16 to effect a heat seal 36 in the region 22. The bag stock 20 
is also cut or separated by the seal head 14 defining the separate bags 37 
thereby. 
FIG. 2 illustrates the apparatus 10 in an indexing mode. That is, the seal 
head 14 has been retracted from the seal roll 16 by lifting the seal tool 
12 in the vertical direction Y3. The bag stock 20 has been indexed a 
distance downstream (to the right) by the rollers 30, 32. The controller 
84 has sent a signal 98 to shift the valve block 95 away from the ports 
73, 91, and to shift the valve block to the ports 73, 91 to register 
therewith. Compressed air is sent through the first pneumatic port 72 to 
an upper region within the cylinder 70. At the same time, the air in a 
lower region of the cylinder can exit the port 90 and discharge to 
atmosphere through the muffler 79 and the exhaust outlet 78. Thus, 
compressed air forces a piston 100 disposed within the cylinder to depress 
the shaft 48 in the direction Y4 to pivot the rocker 40 clockwise to 
release the brake roll 58 from the stop 110 and at the same time to turn 
the drive pulley 60 clockwise a preselected amount. Accordingly, the belt 
66 is driven by the drive pulley 60 to rotate the roll pulley 62 and thus 
the seal roll 16 by a preselected angular amount. Thus, an indexing of the 
roll 16 has been accomplished so that the equipment can next return to the 
condition shown in FIG. 1 and the heat seal head 14 can be descended upon 
the roll 16 at a new location around the circumference of the roll 16. 
Because the roll 16 has been rotated, the landing line 118 of the heat 
seal head 14 on the roll 16 is different for successive heat seals. The 
preceding landing line on the roll is thus allowed to cool before 
eventually being positioned beneath the heat seal head again, and a heat 
build up, and high localized temperature, at the landing line 118 is 
avoided. 
Because the landing line 118 is thus frequently changed on the seal roll, 
excessive wear at any one location is avoided. Also, advantageously, the 
belt 66 is a non-synchronous belt, that is the belt is toothless, and a 
small amount of slippage or float occurs between the belt and the 
associated pulleys 60, 62 during circulation. This effectively further 
changes the exact landing line location on the seal roll, introducing some 
degrees of randomness, so that an exact landing line 118 is not repeatedly 
used during indexing over a period of time. This achieves a more even wear 
of the seal roll 16. 
To return to the position of FIG. 1, the controller sends the signal 82 to 
the four-way valve 74 to deactivate the solenoid actuator 97. Under 
influence of the spring 92, block 96 shifts away from the ports 73, 91 and 
block 95 shifts to the ports 73, 91 to register therewith. Pressurized air 
80 is admitted to a lower region of the cylinder 70 via the channel 95b 
and the second pneumatic port 90. At the same time, air is exhausted from 
an upper region of the cylinder 70 through the port 72, the channel 95a 
and the muffler 79. The piston 100 within the cylinder 70 will then be 
raised in the direction Y2 as shown in FIG. 1, and the apparatus is 
shifted to the braking position shown in FIG. 1, ready for another heat 
seal to be applied to the bag stock. 
An overrunning clutch 120 is arranged between the rocker 40 and the drive 
pulley 60. Overrunning clutches are well known and are available in 
varying styles as understood by one skilled in the art. The overrunning 
clutches as shown in FIGS. 3 and 4 includes a plurality of spring-loaded 
rollers 126 within contoured wedge spaces 130 formed around a clutch plate 
134. The clutch plate 134 is connected by a keyed shaft 136 to the rocker 
40. The shaft 136 is keyed both to the clutch plate 134 and to the rocker 
40 to ensure mutual rotation between the two parts. 
As shown in FIGS. 2 and 4 when the rocker 40 is turned in the rotary 
direction A via the shaft 136, the clutch plate 134 is turned in the 
direction A and the rollers 126 engage tightly within the recesses 130 and 
an inside circumferential surface 140 of the drive pulley 60. The clutch 
plate 134 thus engages the drive pulley 60 for rotation therewith. The 
rocker 40 and the drive pulley 60 thus rotate together clockwise as seen 
in FIG. 2. 
When the rocker 40 is rotated in the rotary direction B as shown in FIG. 1, 
the rollers 126 disengage from the inside surface 140 of the drive pulley 
60 and the rocker rotates in the direction B alone, without driving the 
drive pulley 60. 
It thus follows that up and down movement of the shaft 48 of the pneumatic 
actuator 46 accomplishes two functions, that is, to engage a braking 
action between the brake roll 58 and the stop 110 and when returned to the 
position shown in FIG. 2, by rotation in the direction A, to turn the 
drive pulley 60 to cause an indexing of the seal roll 16. Thus, when the 
heat seal head 14 returns downwardly to press the bag stock 20 against the 
seal roll, a new landing location is presented. 
The speed and angular displacement, or index amount, of the seal roll is 
determined by the pressure and duration of the air supply to the cylinder 
70. For bag making operation, a pressure of 50 psig and a start signal 98 
at 325.degree. and an ending signal 82 at 355.degree. are advantageous. 
The degrees are relative to the rotation of the wicketer arm 39 being 
horizontally disposed beneath the bag 37 at 360.degree. (or 0.degree.) and 
rotated clockwise in FIG. 1. If the pressure of the air is reduced, the 
timing must be advanced to compensate for the slower acting cylinder. 
From the foregoing, it will be observed that numerous modifications and 
variations can be effected without departing from the spirit and scope of 
the novel concept of the present invention. It is to be understood that no 
limitation with respect to the specific embodiments disclosed herein is 
intended or should be inferred. The disclosure is intended to cover by the 
appended claims all such modifications as fall within the scope of the 
claim.