This disclosure is directed to equipment for producing disposable wipes, more particularly, to stacking folded wipes, and more particularly, to a packing apparatus and method for forming stacks of folded wipes. Equipment for producing disposable wipes typically comprises a section for unwinding parent rolls of substrates such as nonwovens or paper into webs of substrate; a section for optionally moistening the webs with a cleaning solution, lotion, or other fluid; a section for folding the webs and interfolding adjacent webs into a continuous ribbon or bolt; a section for cutting the continuous ribbon or bolt into segments or clips of several wipes; a section for combining clips into stacks of a desired number of wipes, this section comprising one or more stackers; and further sections for packaging the stacks of wipes. Within a stacker, to begin the stacking process, a packer transfers segments or clips of cut web material travelling horizontally from the discharge of the cutting section onto a stack below the travel path. The first clip in a stack is transferred onto count fingers. Subsequent clips are transferred onto the previous clip in the stack. After the last clip is transferred onto the stack, the process is repeated with a further set of count fingers.
The clips travelling horizontally from the discharge of the cutting section have a high horizontal velocity and zero vertical velocity. In a short time span, and over a short distance, the clips transition to zero horizontal velocity and a low vertical velocity as the stack is formed. In order to maximize the productivity of the equipment for producing disposable wipes, a packer which makes this velocity transition as smooth as possible, and whose kinematics allow for high cutting and stacking rates, is desired.
In the description that follows, the terms horizontal, vertical, up, down, left, right, and clock positions are used for ease of description and illustration with reference to the drawings and not in any limiting sense.
Without being limited to any specific theory, it is believed that there are at least four primary motion considerations for enabling the kinematics of a packer to allow for high cutting and stacking rates. First, its motion profile should provide for it to be physically out of the way of subsequent clips. Second, when the shoe of the packer makes initial contact with the clip, the face of the shoe which contacts the clip should be approximately horizontal. Third, when the shoe ceases to have contact with the clip, the face of the shoe which contacts the clip should be approximately horizontal. Small deviations from horizontal are permissible in both instances, especially to the extent that this compromise provides for an increase in another benefit. Fourth, the return path that the shoe travels between when it ceases to have contact with a clip and engages with a subsequent clip should be as short as possible.
Prior art packers 30,32,34,36 as shown in
The packer of the present disclosure satisfies all of these criteria. Making reference to
The shoe 52 of the packer 50 is adapted and configured to contact the segment 54 and push the segment onto the stack 56 of segments cut from the web of the material, which may be either the count fingers for the first clip or the stack for successive clips. The shoe 52 may adapted and configured to contact the face of the segment 54 and push the segment onto the stack of segments cut from the web of the material. The packer has a support structure 58 for maintaining the spatial arrangement of the elements and components of the packer and the stacker. A follower 60 may be operatively connected to the shoe 52. The follower 60 and shoe 52 may have an adjustable connection 62 to allow fine tuning and setting of a spacing between the shoe and the follower and the stroke of the follower and shoe.
The packer 50 may also include a drive shaft 70 operatively connected to a motor 72. The drive shaft 70 may be rotatable about a drive shaft center axis 74. The drive shaft 70 may be coupled to the motor 72 with a drive belt and pulley system 76. The motor may be a servo motor, variable frequency motor or any other motor allowing for speed control.
A first drive crank 80 may be operatively mounted to the drive shaft 70 and may be offset from the drive shaft center axis 74. As shown in the drawings, the first drive crank 80 is disposed on an axial end of the drive shaft 70 and the pulley 76 is disposed on an intermediate region of the drive shaft. Other arrangements are also possible depending upon the support structure for the packer. The first drive crank 80 may be operatively pivotally connected to the follower 60. The first drive crank 80 is mounted to the drive shaft 70 so as to rotate together with the drive shaft. Thus, in normal operation, the first drive crank rotates 360 degrees when the drive shaft rotates through 360 degrees. In other words, the first drive crank is mounted to the drive shaft so as to complete one revolution with one revolution of the drive shaft.
A second drive crank 82 may be operatively mounted to the drive shaft 70 and may be offset from the drive shaft center axis 74. As shown in the drawing, the second drive crank 82 is mounted to one axial end of the drive shaft and the first drive crank 80 is mounted an opposite end of the drive shaft with the drive pulley 76 between. Other arrangements are also possible depending upon the support structure for the packer. The second drive crank 82 is mounted to the drive shaft so as to rotate together with the drive shaft. Thus, in normal operation, the second drive crank 82 rotates 360 degrees when the drive shaft rotates through 360 degrees. In other words, the second drive crank is mounted to the drive shaft so as to complete one revolution with one revolution of the drive shaft.
Preferably, the drive cranks 80,82 have a set angular arrangement so as to provide coordinated motion of the follower and shoe as will become evident from the discussion that follows. As shown in the drawings and by way of illustration and not in any limiting sense, the first drive crank 80 is mounted to the drive shaft 70 in a first position and the second drive crank 82 is mounted to the drive shaft 70 in a second position where the first position is offset from the second position by an angle of between 150 degrees and 210 degrees. More preferably, the first position is offset from the second position by an angle of about 180 degrees.
The packer also includes a motion control shaft 90. The motion control shaft 90 may have a center axis 92. The motion control shaft center axis 92 may be aligned parallel to and spaced from the drive shaft center axis 74. The motion control shaft 90 may be mounted for rotary motion within the support structure 58 of the packer and may be arranged vertically between the drive shaft 70 and the shoe 52. The motion control shaft 90 may have first and second rocker arms 94,96 extending outward from the motion control shaft. The first rocker arm 94 may be mounted to one end of the motion control shaft 90 and the second rocker arm 96 may be mounted to an opposite end of the motion control shaft. Preferably, the first and second rocker arms 94,96 have a set angular arrangement so as to provide coordinated motion of the follower 60 and the shoe 52 as will become evident from the discussion that follows. As shown in the drawings and by way of illustration and not in any limited sense, the first rocker arm 94 is mounted to the motion control shaft 90 in a first position and the second rocker arm 96 is mounted to the motion control shaft in a second position where the first position is offset from the second position by an angle of between 60 degrees and 120 degrees. More preferably, the first position is offset from the second position by an angle of about 90 degrees.
A motion control drive linkage 100 may extend between the second drive crank 82 and the first rocker arm 94. The motion control drive linkage 10 may have opposite ends. One end of the motion control drive linkage may be pivotally connected to the second drive crank 82. An opposite end of the motion control drive linkage 100 may be pivotally connected to the first rocker arm 94. A motion control strut 102 may extend between the second rocker arm 96 and the follower 60. The motion control strut 102 may have opposite ends. One end of the motion control strut 102 may be pivotally connected to the second rocker arm 96. An opposite end of the motion control strut 102 may be pivotally connected to the follower 60.
The motion control drive linkage 100 causes rotary movement of the first and second rocker arms 94,96. However, the arrangement is such that the rocker arms 94,96 oscillate along an arc segment between angular positions and do not complete revolutions about the motion control center axis 92 during rotation of the drive shaft 70. The first rocker arm 94 may be mounted on the motion control shaft 90 so as to oscillate on an arc segment of between 60 degrees and 120 degrees when the drive shaft rotates one complete revolution. The second rocker arm 96 may be mounted on the motion control shaft 90 so as to oscillate on an arc segment of 60 degrees and 120 degrees when the drive shaft rotates one complete revolution. Making reference to the orientation of the packer shown in
In an alternative configuration, the second drive crank 82, the motion control shaft 90 and the rocker arms 94,96, the motion control drive linkage 100, the motion control strut 102 may be eliminated and replaced with a motion control drive mechanism that stabilizes the follower and shoe to satisfy the criteria discussed above. For instance, an independent servo motor may replace the second drive crank 82, the motion control shaft 90, the rocker arms 94,96, and the motion control drive linkage 100, and the independent servo motor may drive a linkage similar to the motion control strut 102 to stabilize the follower and shoe to satisfy the criteria discussed above. A gear train or chain drive with or without linkages may also be used.
Making reference to
The lengths of the follower, motion control drive linkage, motion control strut, the first and second drive cranks, and the first and second rocker arms, their respective connection locations, and spatial orientations may be altered as needed from that shown in the drawings to provide for a more optimal combination of smooth velocity transition and kinematics for high speed than is possible with prior packer designs.
Further embodiments can be envisioned by one of ordinary skill in the art after reading this disclosure. In other embodiments, combinations or sub-combinations of the above-disclosed invention can be advantageously made. The example arrangements of components are shown for purposes of illustration and it should be understood that combinations, additions, re-arrangements, and the like are contemplated in alternative embodiments of the present invention. Thus, various modifications and changes may be made thereunto without departing from the broader spirit and scope of the invention as set forth in the claims and that the invention is intended to cover all modifications and equivalents within the scope of the following claims.
This application claims the benefit of U.S. provisional application Ser. No. 63/122,617, filed Dec. 8, 2020, the disclosure of which is incorporated by reference herein.
Number | Date | Country | |
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63122617 | Dec 2020 | US |