Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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This invention relates to a material guide assembly for
use with apparatus for feeding stock material intermittently to a
press, the apparatus generating intermittent feeding of the stock
material by oscillating rotational movement of a driven feed roll
through a preselected angle of rotation.
This application is a divisional application of applicant's
Canadian application Serial No. 368,301, filed January 12, 1981.
It is the conventional practice in high speed automatic
press operations to feed a strip of stock material from a coil to
the dies of the press for punching, stamping, cutting or the like,
at a preselected length of the stock material. The stock material
must be fed from the coil in timed relation with the press operation
so that before the dies contact ~he stock material, the stock
material is moved into a final position by the die pilots as the
feed rolls are released from engagement with the stock material.
The stock material is then stationarily positioned between the dies.
After the press operation is completed, the feed rolls are actuated
to advance another length of the stock material to the press.
Therefore, the feeding of the stock material to the press must be
coordinated with each press operation so that prior to each operation
a new segment of stock material is in position relative to the dies
for the press.
United States Patents 4,133,216 and 4,138,913 are examples
of one type feeding apparatus for power punch presses in which the
feed rolls are drivingly connected by a plurality of meshing gears
to an input shaft drivingly connected to the punch press crankshaft.
A gear cammed drive receives continuous, uniform rotation from the
input shaft and converts the rotation to a noncontinuous step-by-step,
intermittent rotational movement to the driven feed roll. With this
arrangement, the feed rolls advance intermittently through a 360
rotational cycle. During the dwell periods of the rotational cycle,
the driven feed roll is not rotated, and the punchinq operation is
carried out. After the punching operation is completed, the feed
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rolls are again incrementa]ly advanced so that another preselected
length of stock material is passed beneath the press.
United States Patents 3,758,011 and 3,784,075 are examples
of another type of incremental feed apparatus that converts continuous
rotation of a drive shaft to contrarotating oscillating movement of
the feed rolls. The drive shaft is connected through a pair of
meshing gears, one of which is arranged eccentrically and is connected
to a lever that is rotated to-and-fro. The pivotal movement of the
lever is transmitted to a shaft that is, in turn, coupled to the
feed rolls. The oscillatory movement of the lever and shaft is
transmitted to the feed rolls to generate a to-and-fro movement. The
feed length can be changed by altering the amplitude of the oscillatory
movement of the feed rolls.
Synchronously with the to-and-fro movement of the feed rolls,
the feed rolls move toward one another into a feed position and move
away from one another into an idling position. The movement of the
feed rolls between the feed and idling positions takes place at the
point where the feed rolls change directions of oscillation. A holding
mechanism for the workpiece is actuated when the feed rolls move from
their feed position into the idling position, and is deactuated when
the rollers move from their idling position into the feed position.
There is need for press feeding apparatus that incrementally
feeds the workpiece to the press by oscillatory movement of a feed
roll generated by the rotation of the press crankshaft in an
arrangement that permits precise adjustments to be made in the feed
length. While it has been suggested to oscillate the feed rolls of a
press feed to incrementally feed the workpiece to the press, the
prior art feeding apparatus require a complex arrangement for
interconnecting the operations of feeding, clamping, and releasing
the feed rolls that require many component parts which necessitate
increased maintenance and replacement of worn parts.
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The material guide assembly of the present invention, is
used in conjunction with apparatus for intermittently feeding a
workpiece that includes an input shaft supported for rotation at a
continuous preselected speed. An output shaft has a first end
portion and a second end portion. Cam drive means drivingly connects
the output shaft first end portion to the input shaft for generating
oscillating rotational movement of the output shaft through a fixed
preselected angle of rotation. Feed means intermittently feeds a
preselected length of the workpiece in a selected direction. A
linkage is drivingly connected at one end to the output shaft second
end portion and at another end to the feed means. The linkage is
operable to transmit the oscillating rotational movement of the
output shaft to the feed means and oscillate the feed means through
a preselected, variable angle of rotation. me feed means is
actuated by the oscillating rotational movement of the linkage to
intermittently advance a preselected length of the workpiece
corresponding to the angle of rotation of the feed means.
The cam drive means includes a cam nonrotatably connected
to the input shaft. A cam follower rides on the cam surface of the
cam and is nonrotatably connected to the first end portion of the
output shaft. The cam continuously rotates with the input shaft and
oscillating rotational movement of the cam follower through a
preselected angular path, for example through a 60 arc. Thus, upon
one complete rotation of the cam, the cam follower is rotated in a
first direction through a preselected angle and is then rotated in
the opposite direction back through the same preselected angle to
the original starting position. At the end of each angle of
rotation of the cam follower, the cam follower experiences a dwell
period. During the dwell period, there is no transmission of
rotation from the cam to the cam follower.
The angular movement of the cam follower in a first
direction generates rotational movement of the feed means, which
preferably includes a feed roll and an idler roll where either roll
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may be driven or both rolls simultaneously driven, to linearly
advance the workpiece a preselected distance. After a preselected
length of the workpiece is fed, the driven feed roll is released
from engagement with the workpiece to permit final positioning of
the workpiece in the press by the pilots of the press dies. ~ clamp
is thereafter engaged and the driven feed roll is released during a
first dwell period, so that rotational movement of the cam follower
in the opposite direction returns the driven feed roll to the
initial feed position for repeating the intermittent feeding of
the workpiece.
Durlng the interval in which the driven feed roll is
rotated back to the initial feed position, the workpiece is engaged
by a clamping mechanism that is operated synchronously with the
feeding of the workpiece and is also driven by the input shaft.
A second dwell period precedes rotation of the driven feed roll to
advance the workpiece. During the second dwell period, the rolls are
returned to engagement with the workpiece, and the material clamp
is released.
The linkage for the oscillating cam feed includes an arm
member nonrotatably secured to the second end of the output shaft.
The arm member includes a longitudinally extending recess slidably
receiving a slide block that is threadedly connected to an adjusting
screw. The slide block is connected to one end of a drive link, and
the drive link is connected at ~he opposite end to the driven feed
roll. In one embodiment, the drive link is connected to the driven
feed roll through a gear train that includes a pair of gears or a
plurality of gears. In a second embodiment, the drive link is
connected directly to the feed roll.
me adjusting screw is rotatably supported on the arm
member~ By rotation of the adjusting screw, the slide block is
longitudinally movable on the slide portion to a preselected position
on the arm member. Thus, the length of travel of the drive link can
be adjusted by moving the slide block to a preselected position on
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the arm member to provide a preselected angular displacement of the
driven feed roll and, in turn to provide a preselected feed length
for a fixed angular rotation of the cam follower and output shaft.
Synchronously with the intermittent feeding of the workpiece,
the driven feed roll is moved into and out of feeding engagement with
the workpiece, and a clamping mechanism is moved into and out of
clamping engagement with the workpiece during ~he dwell cycle, mus,
during the interval in which the driven feed roll is rotated back to
its starting position to feed the next length of the workpiece, the
driven feed roll is released from engagement with the workpiece,
and the clamping mechanism is moved into engagement with the workpiece.
The feed roll releasing and the workpiece clamping mechanisms
are actuated by a pair of cams that are connected to the input shaft
in a preselected angular position by an adjustable connection. The
idler feed roll is connected by a second linkage to a follower that
rides on the surface of one of the cams. me clamping mechanism is
also connected through a linkage to a follower that engages the
surface of the second cam. Thus upon rotation of the input shaft,
the pair of cams are continuously rotated to actuate the idler feed
roll to move into and out of engagement with the workpiece synchronously
with the movement of the clamping mechanism into and out of clamping
engagement with the workpiece.
During the intermittent feeding of the workpiece, the driven
and idler feed rolls engage the workpiece, and rotation of the driven
feed roll by oscillation of the feed cam forwardly advances a
selected length of the workpiece.
After the selected length of the workpiece is fed and
during the first dwell period of the feed cam, the idler feed roll
is released from engagement with the workpiece. The position of
the workpiece in the press is finally adjusted by the die pilots.
The clamping mechanism is then actuated to engage the workpiece.
As the feed cam is oscillated in the opposite direction to return
the driven feed roll to its initial position for feeding, the driven
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and idler feed rolls are removed from feeding engagement with the
workpiece. During this interval, the workpiece is maintained
secured by the clamping mechanism. During the second dwell period
of the feed cam, the driven and idler feed rolls are first returned
to feeding engagement with the workpiece, followed by the steps
of releasing the clamping mechanism from engagement with the workpiece.
The present invention relates to a material guide assembly
for controlling the feeding of stock material comprising, a machine
frame, a movable material guide movably positioned on the machine
frame, a stationary material guide supported by the machine frame
and fixed relative to the movable material guide, the stationary
material guide being spaced oppositely of the movable material guide
to permit feeding of the stock material between the movable and fixed
material guides, support means mounted on the machine frame for
supporting the movable material guide for movement to a preselected
position spaced oppositely from the stationary material guide, the
support means being adjustable to provide a preselected spacing of
the movable material guide from the stationary material guide so that
the feed of stock material of a preselected thickness is maintained
along a substantially linear path.
me features of the present invention will be more completely
disclosed and described in the following specification, the
accompanying drawings, and the appended claims.
Figure 1 is a partial sectional fragmentary view in side
elevation of a first embodiment of the cam feed apparatus for
drivingly connecting an input shaft to a feed roll to generate a
preselected degree of rotation of the feed roll for a selected feed
length of a workpiece.
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Figure 2 is a fragmentary view tc~ken along line II-II of Figure
1, illustrating a linkage assembly that generates oscillating rotational
move~ent of the feed roll through a preselected angle of rotation.
Figure 3 is a fragmentary, plan view, partially in section, of
the cam drive colmection of the feed press input shaft to an output shaft
for driving the feed roll shown in Figure 1, illustrating a right angle
connection of the input shaft to the output shaft.
Figure 4 is a fragmentary end view of the apparatus for syn-
chronously moving the feed and idler rolls, which are not shown in Figure
4, into and out of engagement with the w~rkpiece, and clamping of the
~orkpiece when the feed roll is released.
Figure 5 is a fragmentary view in side elevation taken along
line ~-V of Figure 4, illustrating the linkages for actuating the opera-
tions of feed roll release and stock material clamping.
Figure 6 is a plan view, partially in section, taken along line
VI-VI of Figure 4, illustrating the arm members for actuating feed roll
release and stock material clamping.
Figure 7 is a view similar to Figure 2, illustrating another
arrangement for connecting a linkage asse~bly to the feed roll.
Figure 8 is a developed partial sectional view in side eleva-
tion of a second embcdiment of the cam feed apparatus, illustrating the
input and output shafts positioned in parc~llel relation.
Figure 9 is a view taken along line IX-IX of Figure 8, illus-
trat-ng the drive connection to the input shaft, and a handwheel for
turning the adjusting screw that controls the position of the drive
link on the transfer arm.
Figure 10 is a fragmentary-view in side elevation of the cam
and cam foll~er arrangem,ent for transmitting oscillatory motion to the
output shaft of the cam feed sh~n in Figure 8.
76
Figure 11 is a sectional view taken along line XI-XI of Figure
10.
Figure 12 is a partial sectional fragmentary view in side
elevation of an adjus~able material guide assembly, schematically illus-
trating the driven feed roll and the idler roll positioned adjacent the
clamp cylinder.
Figure 13 is a schematic view in side elevation of the adjusting
mechanism for adjusting the elevation of the tcp plate of the material
guide shown in Figure 12.
Referring to the drawings, and particularly to Figures 1 and 2,
there is illustrated a first embodiment of apparatus generally designated
boy the numeral 10 for feeding a w~rkpiece such as continuous stock mate-
rial from a reel to a power operated press, as for ex~mple a press for
stamping, punching, cutting or the like, of a preselected length of mate-
rial from the workpiece. ~he apparatus 10 includes a suitable housing 12
and an input shaft 14, illustrated in greater detail in Figure 3. The
input shaft 14 extends through the housing 12 and is supported for rota-
tion therein. The input shaft 14 is drivingly connected to the crankshaft
(not shown) of the press in a manner as illustrated in United States
Patent 4,138,913. Rotation of the crankshaft is transmitted to the input
shaft 14 to rotate the input shaft at a continuous preselected speed.
~ ontinuous rotation
of the input shaft 14 is transmitted by a cam feed mechanism generally
designated by the numeral 18 in Figures 1, 2 and 3 to a driven feed roll
16. The driven feed roll 16 and an idler roll 17 are operable, as will be
explained later in greater detail, to advance a preselected length of the
stock material at a preselected speed to a press where the stock material
is desirably treated, that is punched, stamped, cut or the like. The
driven feed roll 16 and the idler roll 17 are positioned in cverlying
relation with the stock material caught between the feed and idler rolls.
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The rotary motion of the input shaft 14 is converted by the cam feed
mechanism 18 to generate noncontinuous, inte~littent, oscillating rota-
tion of the driven feed roll 16 through a preselected degree of rotation
to intermittently feed a preselected length of the stock material to the
press.
The cam feed mechanism generally designated by the numeral 18
is operable to effect a change in the rate of linear feed of the stock
material to the press and/or to change the length of feed of the stock
material to the press. The cam feed mechanism 18 includes, in part, a cam
20 drivingly connected to the input shaft 14 to rotate continuously at the
rate of rotation of the input shaft 14. The cam 20 includes a cam track
21 that is arranged to receive a cam follcwer 22 that is secured adjacent
to the periphery of a circular cam plate 24. The cam plate 24 is axially
and nonrotat~bly secured to a first end 26 of an output shaft 2~ that is
rotatably supported by bearings 30 in a bearing housing 32. The output
shaft 28, as seen in Figure 3, i5 positioned perpendicular or at a right
angle to the input shaft 14. An arrangement for positioning the shafts
28 and 14 in parallel relation is illustrated in Figure 8 and will be
described hereinafter in greater detail.
The bearing housing 32 is secured to the housing 12 by bolts
34. The output shaft 28 includes a second end 36. A suitable oil seal
38 is positioned between the output shaft second end 36 and the bearing
housing 32 to seal the bearings 30. At the opposite end 26 of the out~
put shaft 28, a spacer 40 is positioned between the bearings 30 and the
cam plate 24 to preload the bearings 30.
With this arrangement, uniform continuous rotatîon of the cam
20 is converted by movement of the cam follower 22 in the cam track 21 of
the cam 20 to oscillating rotationai movement of the cam plate 24 through
a preselected angle of rotation. As for example, as the cam follower 22
follcws the cam track 21 of the cam 20 doring one revolution of the cam
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20, the cam plate 24 rotates from an initial position through an angle
of 60. The cam plate 24 stops during a first ~ell period of rotation
of the cam 20 and then resumes rotation in the opposite direction through
an angle of 60. The cam plate 24 is returned to its initial starting
position and is stopped during a sec~na dwell period of rotation of the
cam 20. I'his is a mcdified slne curve-type cam feed which con~ensates
for the inertia of the moving stock material by accelerating the stock
from an initial rest position to a maximum feed rate and then decelerating
the stock from the maximum feed rate to the rest position.
m e oscillation of the cam plate 24 from an initial position
through a preselected angle and then back through the same angle to the
initial position occurs in one complete revolution of the cam 20. By
continuously rotating the cam 20, the cam plate 24 is continuously
oscillated back and forth through a preselected angle of rotation. At
the end of each angle of rotation, the cam plate 24 experiences a dwell
period in which the plate 24 does not move.
m e oscillating movement of the cam plate 24 is transmltted by
the output shaft 28 to a linkage assen~ly generally designated by the
numeral 42. The linkage assembly 42 includes, in part, a transfer arm 44
that is nonrotatably connected to the output shaft seoond end 36 by dcwel
pins 43 and cap screws 45. The transfer arm 44 slidably supports a slide
block 46 that is connected to a drive link generally desiynated by the
numeral 48. As illustrated in Figures 1 and 2, the transfer arm 44 is
suitably connected to the output shaft 28 in a manner where the inter-
section of the transverse and longitudinal axes of the transfer arm 44 is
coaxially aligned with the axis of rotation of the output shaft 28.
The transfer arm 44 has an elongated body portion 54 with a
longitudinal recessed portion 56. The slide block 46 is longitudinally
movable in the recessed portion 56. The slide blocX 46 is mov~ble in the
recessed portion 56 by rotation of an adjusting screw 50, shown in Figure
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2, having end portions 52 an~ 53. ~nd portion S~ e~xtends through aligne~
bores of a cover plate 58 and an end block 60. Cover plate 5~ is suitably
secured to end block 60, and end block 60 is secured to transfer arm 44 by
threaded member 62. A backplate 64 is connected by threaded members 66 to
the transfer arm 44. The end block 60 is stationarily connected to
backplate 64 by threaded member 68.
The slide block 46 includes a two part or bifurcated end 70
having a bore 72 through one part and arranged to threadedly receive the
adjusting screw end portion 53. A clamp bar 74 abuts the backplate 64 and
is positioned in overlying spaced relation with the adjusting screw 50.
The clamp bar 74 is, in turn, connected by threaded members 76 to the
backplate 64.
By rotation of the adjusting screw end portions 52, the slide
block end portion 70 is advanced longitudinally on the adjusting screw 50
to move the slide block 46 to a preselected position in the recessed
portion 56. In this manner, the slide block end portion 70 is n~oved to a
preselected position relative to the rotational axis of the output shaft
28. The slide block 46 is accordingly movable by releasing the clamp bar
74 from frictional engagement with the surface of slide block end portion
70. The slide block 46 is retained in a preselected position on the
transfer arm 44 by securing the clamp bar 74 in frictional contact with
the surface of the slide block end portion 70. Thus, by selectively
Fositioning the slide block end portion 70 on the adjusting screw 50 a
preselected distance from the axis of rotation of the output shaft 28, it
is possible to adjust the length of travel of the linkage assen~ly 42 to
provide a preselected degree of rotation of the driven feed roll 16 and,
.. I
accordingly, provide a preselected feed length for a fixed angular
rotaeion of the output shaft i8.
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The slide block bifurcated end portion 70 includes a transverse
bore 78 shcwn in E~igure 1, that is aligned with a bore 80 in end portion
82 of drive link 48. ~ clevis pin 84 extends through the aligned bores
78 and 80. A set screw 86 (Figure 2) extends through end portion 70
to engage a flat of clevis pin 84 to prevent pin 8~ frcm rotating in
a bearing (not shown) retained in bore 80. In this manner, the drive
link 48 is connected to the slide block 46. An opposite end 88 of the
drive link 48 is eccentrically connected adjacent to the periphery of
an enlarged gear 90. The enlarged gear 90 is rotatably mounted on a gear
shaft 92 that is secured to the housing 12 by a cap screw 94 extending
through a clamp ring 96 into the housing 12. A bearing nut 98 threadedly
engages the gear shaft 92 to retain the gear 90 on the gear shaft 92,
and a bearing assembly 100 rotatably supports the gear 90 on the gear
shaft 92.
As illustrated in Figure 1, the drive link end portion 88 is
formed by a pair of parallel spaoed arm members 102 and 104 which are
connected by suitahle fasteners 106 (Figure 2) to the drive link end
portion 82. The arm members 102 and 104 are connected to the gear 90 by a
clevis pin 108 extending through a pair of bores 110 and 112 aligned with
an aperture 114 in the gear 90. The clevis pin 108 extends through a
roller bearing assem~ly 116 retained in the aperture 114 of the gear 90.
The arm members 102 and 104 are spaced from the roller bearing assembly
116 by a thrust bearing 118. The clevis pin 108 is retained in the
aligned bores 110 and 112 and roller bearing asse~hly 116 by a set screw
120 (Figure 2) that extends through arm member 102 into contact with the
clevis pin 108. The clevis pin 108 Is also provided with a grease fitting
122 for supplying lubricant to the area around the clevis pin 108 in the
roller bearing assembly 116.
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The enlarged gear 90 includes a plurality of apertures 125, inaddition to aperture 114, that are positioned at a preselected radial
distance from the axis of rotation of the gear shaft 92. The drive link
4~ may also be connected to the enlarged gear 90 by extending the clevis
pin 108 through a preselected one of the apertures 125. In this manner,
different portions of the gear 90 are placed in mesh with the drive gear
124 of the feed roll 16 so as to prevent accelerated wear of one segment
of the gear 90 and permit wear of the gear teeth to be uniformly distri-
buted around the entire gear 90.
The enlarged gear 90 is positioned in meshing relation with a
reduced gear 124. The reduced gear 124 is nonrotatably connected by a nut
126 to the threaded end of a shaft 128 extending axially frcm the driven
feed roll 16. The driven feed roll 16 is suitably supported for rotation
in the housing 12. The oscillating angular movement of the output shaft
28 is thus transmitted by the drive link 48 to the enlarged gear 90.
Therefore, for a given fixed angle of oscillation of the output shaft 28,
the enlarged gear 90 will also oscillate through a preselected angle of
rotation as determined by the longitudinal position of the slide block 46
on the transfer arm 44 and the length of travel of the drive link 48. By
adjusting the position of the slide block 46, the length of travel of the
drive link 48 is adjustable. In this manner, it is possible to provide
for a variation in the angular movement of the driven feed roll 16 and a
change in the feed length.
The driven feed roll 16 cooperates with idler roll 17 to feeà
the stock material, for example, to the dies of the punch press. The
idler roll 17 is operable to periodically move away from the driven feed
roll 16 and permit the driven feed roll 16 to oscillate back to its
initial position for feeding the stock material during the punching
operation. The idler roll 17 then moves back toward the driven feed roll
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16 in order to permit the next increment of the stock material to be fed
to the dies of the punch press. The idler roll 17 is fixed to a rota-
table shaft (not shown) in a manner as disclosed in United States Patent
3,977,589, which is inoorporated herein by reference. The rotatable shaft
is journaled within a frame which is rotated about an axis to ve the
idler roll 17 toward and a~lay from the driven feed roll 16. The rotatable
shaft and frame will not be described in detail for the present invention~
Where desired, the linkage assenbly 42 may be connected to the
driven feed roll 16, as illustrated in Figure 7 and to be discussed later
in greater detail, and the gear train ccmprising gears gO and 124 deleted.
However, by utilizing the meshing gears 90 and 124 to transmit the oscil-
lating rotational movement to the driven feed roll 16, it is possible to
rotate the driven feed roll 16 through an angle greater than the angle of
rotation of the output shaft 28. This permits an increase in the feed
length over a feed length which would result from rotating the driven feed
roll 16 through an angle corresponding to the angle of rotation of the
output shaft 28. Accordingly, the gear ratio used will also determine the
feed length.
Adjustments in the feed length are easily made by changing the
length of travel of the drive link 48 or by adding additional gears to the
gear train connecting the drive link 48 to the feed roll 16. The length
of travel of the drive link 48 is adjusted by changing the distance
between the axis of rotation of output shaft 28 and the connection of the
drive link 48 to the transfer arm 44. By moving this connection tcward
the axis of rotation of output shaft 28, the angular displacement of the
driven feed roll 16 is decreased. Accordingly, the feed length is de-
creased. Thus, with this arrangement, very accurate adjustments can be
quickly made in the feed length without the time consuming operation of
changing feed rolls of different diameters.
?76
In operation, for example during clockwise rotation of the
driven feed roll 16 corresponding to the fixed angle of rotation of the
output shaft 28, for example 60~, a preselected length of the stock
material is fed by rotation of the driven feed roll 16. After completion
of the angular movement of the driven feed roll 16, a first dwell period
occurs during which time the driven feed roll 16 and the idler roll 17
are released from driving engagement with the stock material, and a
clamping mechanism generally designated by the numeral 130 in Figures 4
and 5 is actuated to prevent movement of the stock material as the driven
feed roll 16 is rotated back to the initial feed position. ~hen the
driven feed roll 16 has rotated counterclockwise through a selected angle
of rotation, a second dwell period occurs during which time the cla~ing
m~chanism 130`is released from engagement with the stock material, and the
driven feed roll 16 and the idler roll 17 are moved back into driving
engagement with the stock material for feeding another increment of stock
material to the press.
Referring to Figures 4 and 5, there is illustrated the clamping
mechanism 130 and a feed release mechanism generally designated by the
numeral 132. The clamping mechanism 130 is positioned adjacent to the
driven feed roll 16 upstream of the feed roll 16 in the feed stock line.
The clamping mechanism 130 and the feed release mechanism 132 are driven
by a clamp release cam 134 and a roll release cam, positioned beyond cam
134 and not shown in Figure 4, respectively.
The clamp release cam 134 and the roll release cam are also
adjustably connected to rotate with the input shaft 14 that extends
through the housing 12. The clamp release cam 134 and the roll release
cam have a cam configuration that coordinates with the configuration of
the feed cam 20, illustrated in Figure 3, so that the feeding of the
stock material is synchronized with the en~agement of the rolls 16 and 17
with the stock material and release of the cla~ping mechanism 130 from
engagement with the stock material.
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By changing the respective angular positions of the clamp
release cam and roll release cam on the input shaft 14 and then securing
the cams in the selected position, it i5 possible to change the sec~ence
of the clamp release and the roll release o~erations to take place during
the first dwell period or the second dwell period, respectively. By
changing the sequence of the clamp release and the roll release opera-
tions, it is possible to change the material feed direction to push the
stock material into or pull the stock material away frcm the press. As
stated a~ve, the cam 20 for controlling the feed of the stock material
to the press is synchronized with the movenent of the clamp release cam
134 and the roll release cam. Therefore, the operation of feeding the
stock material can take place upon rotation of the cam plate 24 and ~utput
shaft 28 in either a clockwise direction or a counterclockwise direction.
~ccordingly, the direction of rotation of the output shaft 28 to actuate
feeding of the stock mate~ial to the press determines during which dwell
periods the operations of clamp release and roll release take place.
The roll release cam is not shcwn, but it should be understocd
it is similar to the cla~p release cam 134 and includes a peripheral cam
surface that supports a cam follower 136, as illustrated, connected to the
end of a cam follcwer arm 138 by a nut and bolt com~ination 139. The cam
arm 138 is pivotally mounted on a pivot pin 140 secured by a set screw 142
in the bore of a lug 144 that is connected to a lift arm 146. m e lift
arm 146 is pivotally unted on one end of a shaft 148 that is retained in
a bore of an upstanding support 150. The shaft 148 is connected at the
opposite end to housing 12. The support 150 is secured by fasteners 152
to a mounting bracket 154. The m~unting bracket 154 is, in turn, con-
nected by fasteners 156 to a side rail 158 that is connected b~ fasteners
160 to a side plate 162 of housing 12.
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I~he lift arm 1~6, as illustrat~d in ~igure 6, is connected at
one end to a roll release screw 164 ~y a lift pin 166 that extends through
aligned bores of the lift ann 146 and the roll release screw 164. The
lift pin 166 is retained by a set screw 168 in ~he aligned bores. As
illustrated in Figure 5, the lcwer end of the roll release screw 164 is
connected to actuator arms 170. The actuator arms 170 are oonnected to a
frame 172 that is supported for rotation within the housing 12. The
details of rotatably supporting the frame 172 in the housing 12 are
disclosed in the above-referenced United States Patent 3,977,589 and
therefore will not be described in detail. The idler roll 17 is suitably
journaled in the frame 172 so that upon rotation of the frame 172 by
movement of the actuator arms 170, the idler roll 17 moves toward and
away from the driven feed roll 16.
As illustrated in Figure 4, on the opposite end of the lift arm
146 is mounted a pivot clamp screw 174 that is positioned in an annular
recess of the lift arm 146. A cap screw 176 extends through the cam
follower arm 138 and the lift arm 146 into threaded engagement with the
pivot clamp screw 174 in order to adjustably clam~o the arms 138 and 146.
An adjusting screw 178 extends thro~gh the end of the lift arm 146 ana
abuts the end of the cam follower arnl 138 to adjustably position the cam
follower arm 138 and cam follower 136 relative to the surface of the roll
release cam (not shown)..
Thus in operation upon rotation of the roll release cam with
the input shaft 14, the cam follower arm 138 is pivoted about pivot pin
148 by the action of the cam follower 136 on the surface of the roll
release cam. The lift arm 146,pivots with the cam follower arm 138
to raise and lower roll release screw 164 and tne actuator arms 170.
During each cycle of the punch press; the actuator ar~ls 170 are actuated
to rai.se the frame 172 and thereby rotate the frame 172 to lcwer the idler
roll 17 a~ay from the driven fe d roll 16. ~his operation is disclosed in
1~7~ 6
greater detail in the above-referenced ~nited States Patent 3,977,589
which is assigned to the assignee of the present invention. Accordingly,
the details of moving the frame 172 to raise and lower the idler roll 17
are beyond the scope of the present invention and are only schematically
illustrated in E`igure 5.
When the idler roll 17 is lowered, the stock material is dis~
engaged frcm the rolls 16 and 17 so that the stock material is not fed
to the punch press during the punching oFeration. Further~ore, during
the interval where there is no material fed to the press, the driven
feed roll 16 is rotated back to the initial position for the feed cycle.
Accordingly, prior to the feed cycle, the frame 172 is rGtated to raise
the idler roll 17 toward the drive feea roll 16 to return the rolls 16
and 17 to driving ensagement with the stock .material.
Synchronously with the movement of the roll release screw 164
and the actuator arms 170, illustrated in Figure 5, to remove the rolls
16 and 17 from driving engagement with the stock material, rotation of the
clamp release cam 134, illustrated in Figure 4, is operable to actuate the
clamping mechanism 130 to engage the stock material during the interval
of angular rotation of the driven feed roll 16 back to the position for
initiating the feed cycle. The clamping mechanism 130 is actuated by
movement of a cam follower 180 on a ca~ surface 182 of the clelmp release
cam 134. The cam follc~er 180 is secured intermediate to a cam arm 184 by
a nut and bolt combination 186. The cam arm 184 is pivotally ~ounted at
one end portion on the shaft 148. The opposite end of the ce~m arm 184 is
provided with an adjusting screw 188 that extends through and below the
cam arm 184. m e adjusting screw 188 is secured in a selected position
on the cam arm 184 by a nut 190.
The lcwer end of the adjusting screw 188, as illustrated in
~igure 4, abuts the top surface of a pressure pad 192. The pressure pad
192 is suitably secured to eln air actuated clamp cylinder 194. The cle~np
- 18 -
117~
cylinder lY4 is position~ for vertical n~vement in a ~re 19~ of the
mounting brac~et 154. The cylinder 194 includes an extensib'e cylinder
rod 198 thcnt ex~ends belcw a clamp support 200 which reclines the lower
end of clamp cylinder 194. The clamp support 200 is positioned for
vertical vement below the mounting bracket 154. A set screw 202 ex-
tends through the clan~ support 200 and into engagement with the lower
end portion of the clan~p cylinder 194~ Thus the cla~ cylinder 194 is
connected to the clan~ supFort 200. The cylinder rod 198 is connected
by threaded engagement with a pad 204 arranged to move into and out of
clamping engagement with the stock material generally designated by
numeral 206 in Figure 4. The feed line of the stock material is indi-
cated by the numeral 208 as shown in Figures 4 and 5.
The stock material 206 is supForted for lon~itudinal move~Rnt
on the surface 210 of a guide plate 212, as illustrated in Figures 4 and
5. The guide plate 212 is horizontally supported by a frame generally
designated by the numeral 214. The frame 214 includes pairs of support
me~ers 216 and 218 that are rigidly connected to the guide plate 212.
The frame 214 is also provided with a base 220. The base 220 is connected
- by bolts 222 to the housing 12.
The pad 204 is shown in Figure 4 in a raised position out of
engagement with the stock material 206. In Figure 5 the pad 204 is also
shown in a raised position; however, the stock material is not shown in
Figure 5. When the pad 204 engages the stock material 205, the material
is fixed to prevent feeding during the punching operation. Accordingly,
when the pad 204 is moved to the raised position, the next increment of
the stock material is fed to thë punch press for the punching operation.
The pad 204 is lowered into clamping position by downward
vertical movement of the clamp cylind~r 194 in response to the pressure
exerted on the pressure pad 192 by downward movement of the adjusting
screw 188. The adjusting screw 188 moves downwardly by downward pivoting
-- 19 --
1~7~ 6
of the cam ~nm 184 on the shaft 148 as the cam follower 180 foll~s the
c~r, surface 182 of the rotating clamp release cam 134. By the application
of downward pressure upon the pressure pad 192, the cl~p cylinder 194 and
the clamp support 200 are moved do~lwardly relative to the fixed mounting
bracket 154. The clamp cylinder 194 is connec~ed by conventional means
(not shown) to a source of air under pressure. In this manner, the air
pressure in the cl~,p cylinder 194 is regulated to maintain a constant
pressure upon the cylinder rod 198 and normally position the rod 198
extended from the cylinder 194. Thus, when the cylinder 194 is moved
downwardly, the rod 198 is fully extended from the cylinder 194. Downward
movement of the cylinder 194 and extended rod 198 moves the pad 204 into
clamping position with the stock ~aterial 206.
A spring return mechanism generally des.ignated by the numeral
224 in Figure 4 is provided to return the pad 204 to the raised position
removed from engagement with the stock material 206 after the clamping
cycle is completed upon continued rotation of the clamp release cam
134. This operation is synchronized with conmence~,ent of the feed cycle
and movement of the rolls 16 and 17 into engagement with the stock mate-
rial 206.
The spring return mechanism 224 includes a pair of bores 226
and 227 extending through the mounting bracket 154 and the clamp support
200, respectively. A bushing 228 is positioned in each bore of the mount-
ing bracket 154. A bolt 230 extends through the respective bushing 228
and into threaded engagement with the clamp support 200. The bolts 230
are each provided with an enlarged head 232, and each bore 226 is pro-
vided with an enlarged diameter upper end portion 234 below the respec-
tive bolt head 232. Selected coil springs 236 are posi,ioned in bore
upper end portions 234 surrounding the bolts 2~0 and abut at one end
the bolt heads 232 and at the opposite end the mounting bracket 154
surrounding the bore upper end portions 234. Thus, the bolts 230 are
positioned for vertical reciprocal movem.ent in the bushing 228 of the
mounting bracket 154.
r
- 20 -
~ ith this arrangement, uFon release of pressure upon the cla~p
cylinder 194 by upward pivoting of the cam arm 184, the clamp cylinder
194 moves upwardly within the bore 196 of the mounting bracket 154 The
coil springs 236, being compressed by the downward movement of the bolts
230 with the clamp support 200 and the clamp cylinder 194 relative to the
fixed mounting bracket 154, are free to extend and thereby raise the bolts
230, together with the clamp support 200, when the downward pressure upon
the clamp cylinder 194 is relieved. The cla~p support 200 ~oves upward
with the bolts 230 upon extension of the coil springs 236. In this
manner, the extended cylinder rod 198 is raised with the cla~p cylinder
194 to remove the pad 204 from cla~ping engagement with the stock material
206. This permits un~m?eded movement of the stock material on the guide
plate surface 210 during the feed cycle of the punch press.
The bolts 230 are vertically movable in the bushings 228 of the
mounting bracket 154 which remains stationary. The clamp support 200 is
movable relative to the mounting brac3~et 154. As illustrated in Figures
4 and 6, the mounting bracket 154 is provided with an upstanding arm 238
having a bore 240 therethrough. A spacer 242 is positioned bet~een the
upstanding arm 238 and the housing 12. The spacer 242 includes a bore
244 which is aligned with the bore 240. The aligned bores 240 c~nd 244
receive a bolt 246 which extends into threaded engagement with housing
12 to further rigidly secure the mounting bracket 154 in a stationary
position.
During the period of roll release, the cla~ release cam 134 is
operative to pivot the cam arm 184 downwardly on the shaft 148 so that the
adjusting screw 188 applies a downward force upon the clamp cylinder 194.
The cylinder 194 moves downwardiy within the bore 196 of the mounting
bracket 154 and compresses the coil springs 236. As described cibove, the
cylinder rod 198 is maintained extended frcm the cylinder 194 by supplying
the cylinder 194 with air at a preselected pressure. The air pressure is
- 21 -
1~'7~5~76
direct~d upon the upper end of the cylinder rod 198. When the cylinder
194 and the rod 198 ~.ove downwardly, the pad 20~ is ~oved into clamping
engagelnent with the stock material 206. During the clamping engagement
of the stock material, the air in the clamp cylinder lg4 is further ccm~
pressed to assure that the pad 204 exerts a preselected pressure upon the
stock material 206 to prevent it fr~m moving on the guide plate surface
210. Thus, the stock material 2U6 is not advanced backwardly during the
cycle when the feed roll 16 is returned to its initial position for the
feed cycle.
Once the driven feed roll 16 has been rotated to its initial
position for commencing the feed cycle, the cam arm 184 is pivoted upward
to the position illustrated in Figure 4. m e coil springs 236 extend to
raise the bolts 230, the clamp support 200, the cylinder 194, the cylinder
rod 198, and the pad 204. The stock material is then free to move beneath
the pad 204 on the surfaoe 210 of the guide plate 212. Thus, it will be
apparent with the present invention that the operations of releasing the
driven feed roll 16 and the idler roll 17 from engagement with the stcck
material and clamping the stock material are coordinated with the oscilla-
ting rotational movement of the output shaft 28 by the c~m feed mechanism
18 as required to carry out the intermittent feeding of the stock material
through the press.
Further, in accordance with the present invention illustrated in
Figure 1, the enlarged gear 90 is mounted on the shaft 92 in a manner to
facilitate the movement of the enlarged gear 90 relative to the reduced
gear 124 shown in Figure 2 and thereby permit adjustments in the meshing
engagement of the gear teeth of gears 90 and 124. The gear shaft 92
includes an elongated body portlon 248 upon which the enlarged gear 90 is
positioned, and a stub end portion 250 which is positioned in a bore 252
of the housing 12. Intermediate the shaft body portion 248 and the shaft
end portion 250 is provided an enlarged diameter portion 254. The axes of
76
the enlaryed di~meter portion 254 and the shaft body portion 248 are
concentric, while the axis of the stub end portion 250 is eccentric
relative to the axes of shaft portions 24~ ana 254.
The shaft stub end portion 250 is held within the bore 252 by
the cla~ ring 96 engaging the enlarged diameter portion 254 and the cap
screw 94 threaded tightly into engagement with the cl~ ring 96 and the
ho~sing 12. When the stub end portion 250 is clamped in position by the
cla~p ring 96, the stub end portion 250 is nonrotatably retained in the
bore 252 of the housing 12. However, by loosening the cap screw 94, the
entire shaft 92 and the shaft stub end 250 can be rotated.
Because of the eccentric relationship between the shaft portions
248 and 250, rotation of the shaft 92 permits the enlarged gear 90 to be
moved laterally relative to the reduced gear 124 of the driven feed roll
16~ This allows the gear teeth of the enlarged gear 90 to be removed into
and out of precise engagement with the gear teeth of the reduced gear 124.
Thus, any backlash existing between the meshing gears 90 and 124 can be
removed by first loosening the clamp ring 96 to permit rotation of the
shaft 92 until the respective meshing gear teeth are engaged in a manner
free of backlash. The gears 90 and 124 are then maintained in the
desired meshing position by securely clamping the cla~p ring 9o into
engagement with the shaft enlarged diameter portion 254 by tightening
of the cap screw 94.
By removing backlash and play between the meshing gears 90 and
124, lost motion is removed in the transmission of rotation from the
linkage mechanism 42. It will be apparent that this arrangement is
particularly advantageous in permitting adjustments in the position of
the enlaraed gear 90 in order to oompensate for machining tolerances
that may exist between various enIarged gears 90 used to replace an
existing gear 90 in the gear train for transmitting rotation from the
output shaft 28 to the driven feed roll 16.
- 23 -
The ability to a~just the position of the enlarged gear 90
obviates the need for precise machinillg of the drive gears so that toler-
ances may be permitted within the range of adjustment that can be made.
miS avoids the need for using expensively manufactured gear trains to
assume that no lost motion exists in the transmission of rotation from the
linkage mechanism 42 to the driven feed roll 16~ Thus with the present
invention, the gear train provides for transmission of rotation free of
lost ~otion between rotation of the output shaft 28 and the driven feed
roll 16.
A further feature of the present invention is illustrated in
Figure 7 where the linkage mechanism 42 is connected directly to the
driven feed roll 16. This arrangement is an alternative to the arrange-
ment shown in Figures 1 and 2 for transmitting rotation from the linkage
mechanism 42 through a gear train of t~ or more gears to the driven feed
roll 16. The feed length for the emkodiment of Figure 7 is also adjusted
by moving the slide blocX 46 on the transfer arm 44 by rotation of the
adjusting screw 50 in the manner described above.
The linkage mechanism 42 in Figure 7 includes a drive link
generally designated by the numeral 256 having a first link portion 258
connected to the slide block bifurcated end portion 70 in a manner similar
to the connection of drive link 48 to the end portion 70 shown in Figure
2. The first link portion 258 is adjustably connected to a second link
portion 260 by a threaded connector 262. The second link portion 26U
is, in turn, connected to a secondary link 264 by a suitable connector 266
extending through aligned b~res in the second link portion 260 and the
secondary link 264. r~te secondary link 264 is connected to the shaft
128 of the driven feed roll 16 in a manner to transmit the oscillatory
movement of the drive link 256 to the driven feed roll 16.
- 24 -
~ 1 7~3~
In this manner, the driven feed roll 16 is rotat~d as above
described for the generating intermittent feeding of the stock material
to the press. With the arrangement of Figure 7, however, the oscillating
rotational movement of the driven feed roll 16 is accomplished without
the provision of the gear train shown in Figure 1. Further, to provide
for the direct linkage connection from the output shaft 28 to the driven
feed roll 16, the transfer arm 44 is angularly displaced on the output
shaft end portion 36 to a preselected position as shown in Figure 7, to
permit the slide block end portion 70 to be directly connected to the
driven feed roll 16 by the drive link 256 and the secondary link 264.
Now referring to Figures 8-11, there is illustrated a second
embodiment of the apparatus 10 for intermittently feeding a workpiece,
such as a sheet material, to a press for stamping, forming, or the like.
It should be understood that many of the features of the second embodi-
ment of the present invention illustrated in Figures 8-11 cvrrespond to
the similar features illustrated in Figures 1-7 and discussed above in
detail.
In the second emkodiment of the pre~ent invention as illustrated
in Figure 9, a first powered input shaft 270 is rotatably supported at its
opposite end portions 272 and 274 by conventional bearing assemblies
generally designated by the numerals 276 and 278, respectively. The first
powered input shaft 270 is continuously rotate~ at a preselected speed by
a suitable drive connection on the end portion 272 in a manner similar to
that discussed for the input shaft 14 described above and illustrated in
Figures 1 and 3. A second powered input shaft 280, which is illustrated
in dotted lines in Figure 9 and ln full in Figure 8, is positioned at a
right angle with respect to the first powered input shaft 270.
The first powered input shaft 270 is drivingly connected to the
second powered input shaft 280 by a pair of meshing gears 282 and 283,
shown in Figure 9. Gear 282 is nonrotatably connect~d to the intermediate
- 25 -
portion of the first input shaft ~70, and gear 283 is nonrotat~hly connec-
ted to a first end portion 284 of the second input shaft 280. The second
pc~ered input shaft 2~0 is also rotatably supported in the machine housing
12 by conventional bearing assemblies generally designated by the numerals
286 and 288. m e second input shaft 280 includes a second end portion
290 that extends from the rear of the housing 12.
It should also be understood that the second emkodiment of the
intermittent feed apparatus 10 also includes a material clamping mechanism
generally designated by the numeral 292 and a feed release mechanism
generally designated by the numeral 294. The respective mRchanisms 292
and 294 correspond to the clamping mechanism 130 and feed release mecha-
nism 132, illustrated in Figures 4 and 5 of the first embodiment and
discussed hereinabove in detail. The clamping mechanism 252 and the feed
release mechanism 294, therefore, operate in substantially the same manner
to produce substantially the same result as above described for the
clamping mechanism 130 and the feed release mechanism 132.
The clamping mechanism 292 and the feed release mechanism 294
are driven by a clamp release cam 296 and a roll release cam 298, illus-
trated in Figure 9. The clamp release cam 296 and the roll release cam
298 are adjustably, nonrotatably connected to the first powered input
shaft 270 as iIlustrated in Figure 9. The operations of the cams 296 and
298 to synchronously feed the stock material with the engagement of the
rolls 16 and 17 with the stock material and release of the clamping
mechanism 292 from engagement with the stock material is carried out in
the manner as above described for the cla~ping mechanism 130 and the feed
release ~chanism 132. Thereforë, these operations will not be discussed
in greater detail for the second embodiment of the intermittent feed
apparatus 10.
- 26 -
1~'7~9'76
The second power input shaft 280 is continuously rotated at a
preselected speed, and the continuous rotation of the second input shaft
280 is converted by a cam drive mechanism generally d~signated by the
numeral 300 to oscillatinq rotational movement of an output shaft 302
which corresponds to the output shaft 28 illustrated in Figure 1 and above
described for the first embodiment of the apparatus 10. The output shaft
302 is positioned m spaced parallel relation to the seo~nd input shaft
280 and is rotatably supported in the housing 12 at its end portions by
conventional bearing assemblies generally designated by the numerals
304 and 306.
The output shaft 302 includes an enlarged end portion 303 which
is nonr~tatably connected by a plu~ality of dowel pins 305 and cap screws
307 to a transfer arm 308 of a linkage assembly generally designated by
the numeral 310. The linkage assembly 310, as above described for the
linkage assembly 42 in Figure 1, is operable to transmit the oscillating
movement of the output shaft 302 to the driven feed roll 16, which is also
illustrated in Figure 8 and corresponds to the driven feed roll 16 illus-
trated in Figure 1.
The cam drive mechanism 300, illustrated in Figures 8, 10, and
11 includes a pair of radial conjugate cams 312 and 314 that are preloaded
against a pair of cam followers 316 and 318 that are rotatably mounted on
a pair of yoXe members 320 and 322, respectively. The cams 312 and 314
have a preselected configuration to convert the continuous rotation of the
second input shaft 280 to oscillating rotational movement of the output
shaft 302. The cams 312 and 314 are nonrotatably connected to the inter-
mittent portion of the second input shaft 280 and are maintained in a
fixed axial position thereon by a shaft collar 324 and a cam spacer 326.
- 27 -
.lL~'7~76
Each of the cam follcwers 316 and 318 is mounted on a pin 328 which i5
rotatably retained in the respective yoke members 320 and 322 to permit
rotation of the cam follcwers 316 and 31~ as the cam followers 316 and 318
move on the peripheral surfaoes of the cams 312 and 314.
As illustrated in Figure 10, the yoke members 320 and 322
maintain the cam follcwers 316 and 318 in contact with the peripheral
surfaces of the cams 312 and 314. Each of the c~s 312 and 314 has a
corresponding configuration to generate oscillating rotational movement
of the yoke members 320 and 322 and as a result, oscillate the output
shaft 302 through a preselected angle of rotation. As for example as
above described for the embcdiment ilustrated in Figure 1, as the cam
followers 316 and 318 follGw the surface of the cams 312 and 314 during
one revolution of the input shaft 280, the yoke members 320 and 322
rotate from an initial position through a preselected angle, as for
exa~ple, an angle of 60.
The yoke members 320 ana 322 and the output shaft 302 stop
auring a first dwell pericd of rotation of the cams 312 and 314, and
then resume rotation in the opposite direction through a corresponding
angle, as for example, an angle of 60. The yoke members 320 and 322 and
the output shaft 302 return to their initial starting position and are
stopped during a second dwell period of rotation of the cams 312 and 314.
By provlding a pair of cams 312 and 314, the inertia of the moving stock
material generated by acceleration o the stock material frc,m an inltial
rest position to a maximum feed rate and then decelerating the stock
material frcm the maximum fèed rate to the rest position is compensated to
maintain constant contact between the cams 312 and 314 and the cam fol-
lowers 316 and 318. This arrangement assures zero backlash during each
rotational cycle.
- 28 -
1~
As above described for the cam plate 24 shown in Figure 1,
the yoke members 320 and 322 and the output shaft 302 oscillate from an
initial position through a preselected angle and then back through the
same angle to the initial position upon each revolution of the cams 312
and 314. Thus, as the cams 312 and 314 continuously rotate, the cam
followers 316 and 318 together with the yoke members 320 and 322 and the
output shaft 302 oscillate back and forth through a preselected angle. At
the end of each angle of rotation, the yoke members 320 and 322 experience
a dwell period in which the yoke members 320 and 322 do not move.
The oscillating movement of the output shaft 302 is transmitted
by the linkage assembly 310 to the driven feed roll 16. ~s illustrated
in Figures 8 and 9, the transfer arm 308 of the linkage assembly 310
overlies the axis of rotation 330 of the output shaft 302. The transfer
arm 308 slidably supports a slide block 332 that is connected to one end
of a drive link generally designated by the numeral 334. As illustrated
in Figure 9, the transfer arm 308 supports the slide block 332 for slid-
able movement along an axis 336 of an adjusting screw 338. The axis 336
of the adjusting screw 338 is transversely aligned with the axis of
rotation 330 of the output shaft 302.
The transfer arm 308 has a longitudinally extending recessed
portion 340 aligned with the adjusting screw axis 336. The slide block
332 is longitudinally movable in the recessed portion 340. The recessed
portion 340 includes a radial groove 342 for receiving the adjusting
screw 338. Positioned opposite the radial groove 342 is a threaded
radial groove 344 in the slide block 332 for threadedly receiving the
adjusting screw 338. As seen -in Figure 9, the adjusting screw 338 is
rotatably sup~orted at its end portions in bearir.g bloc~s 346 an~ 348
which are secured to the transfer arm 308. With this arrangement, the
adjusting screw 338 is rotatable relative to the transfer arm 308 but is
- 29 -
1~7~g~7f~
restrained from axial n~vement relative to the transfer arm 308. ~pon
rotation of the adjusting screw 33B in a preselected direction, the slide
bloc~ 332 moves longitudinally in the re oessed portion 340 to a prese-
lected position on the transfer arm 308.
A shaft 350 having a threaded end 352 is formed integral with
the slide block 332 and extends outwardly therefran. A clamp bushing 354
is positioned on the shaft 350. The clamp bushing 354 includes a plate
end portion 356 that is slidable in a longitudinally extending recessed
portion 358 of the transfer arm 308. l'he recessed portion 358 is posi-
tioned parallel to the recessed portion 340 on the slide blocX 332 where
the recessed portion 358 extends the length of the recessed portion 340.
A shaft portion 360 extends frcm the plate end portion 356, and the slide
block shaft 350 extends through a bore of the shaft portion 360.
The drive link 334 includes a first end portion 362 and a second
end portion 364. The first end portion 362 has a bore therethrough in
which is positioned a bushing 366. The bushing 366 is positioned on the
,shaft portion 360. The drive link first end portion 362 is retained on
the shaft portion 360 by a nut 368 that threadedly engages the shaft
threaded end 352. The nut 368 tightly engages the threaded end 352 to
urge the clamp bushing 354 into frictional engagement with the transfer
arm 308 to thereby retain the slide block 332 in a preselected position on
the transfer arm 308 relative to the point of intersection of adjusting
screw axis 336 and the rotational axis 330 of the output shaft 302.
As illustrated in Figures 8 and 9, the drive link second end
portion 364 is connected through a pair of meshing gears 370 and 372 to a
shaft 374 of the driven feed roil 16. Hc~ever, it should be understood
that the drive link 334 can be directly connected to the driven feed roll
16 in an arrangement as illustrated in Figure 7 and described above. With
the arrangement in Figure 9, the meshing gears 370 and 372 transmit
- 30 -
~7iD~76
oscillating novement of the drive link 334 to the driven feed roll 16~ By
connecting the drive link 334 to the shaft 374 of the driven feed roll 16
either directly or through meshing gears, the oscillating rotational move-
ment of the output shaft 302 is transmitted to the driven fe~d roll 16 to
thereby rotate the driven feed roll 16 through a preselected angle cor-
responding to a preselected len~th of the workpiece to be fed to a press.
'~he length of travel of the drive link 334 generated by the
oscillating rotational movement of the output shaft 302 is adjustable,
as above discussed, to provide a preselected degree of rotation of the
driven feed roll 16 corresponding to a preselected feed length, as a
result of the fixed angular rotation of the output shaft 302. The length
of travel of the drive link 334 and accordinqly the degree of rotation of
the driven feed roll 16 and the resultant feed length increases with an
increase in the distance between the connection of the drive link first
end portion 362 on the transfer arm 308 and the rotational axis 330 of
the output shaft, as illustrated in Figure 9.
In Figure 9, the drive link first end portion 362 is con-
nected to the transfer arm 308 in a position substantially spaced from
the rotational axis 330 to provide substantially a maximum feed length.
Accordingly, to reduce the feed length, the drive link first end portion
362 is moved on the transfer arm 308 to a position closer to the rota-
tional axis 330. In this manner, the feed length of the stock material
to the press is substantially, infinitely adjustable ana is acco~plished
by rotation in a preselected direction of the adjusting screw 338.
To make adjustments in the feed length, the nut 368 is loosened
on the shaft threaded end 352 to thereby remove the cla~p bushing plate
end portion 356 fr~m frictional engagement with the surface of the trans-
fer arm 308 in the recessed portion 358. The adjusting screw 338 is then
rotated in a preselected direction on the transfer arm 308 by a spring
- 31 -
?7~
loaded actuating device generally designated by the numeral 376 in Figure
9. The actuating device 376 includes a hand wheel 378 nonrotatably
oonnected to the end of a shaft 380 that is positioned for rotational
and axial movement in a block 382 that is secured to the housing 12.
A socket 384 is connected to the op~osite end of the shaft 380
and is movable longitudinally through a bushing 386 positioned within a
bore 388 that extends through the end of the block 382. The socket 384 is
normally maintained in spaced axial relation opposite the head of the
adjusting screw 338 of the transfer arm 308 by a c,~mpression spring 390.
The spring 390 abuts at one end against a bearing sleeve 392 through which
the shaft 380 extencls in the block 382 and at an opposite end against the
hand wheel 378 that is axially fixed on the opposite end of the shaft 380.
In operation, the length of travel of the drive link 334 is
adjusted by adjusting the position of the drive link end portion 362 on
the transfer arm 308. The adjusting screw 338 is rotated by the actuating
device 376 to adjust the position of the drive link end portion 362 on the
transfer arm 308. This is acc,~mplished by nonrotatably connecting the
socket 384 with the end portion 394`of the adjusting screw 338. By
exerting an axial force upon the hand wheel 378 t the spring 390 is cc~r
pressed between the hand wheel 378 and the bearing sleeve 392. This
advances the shaft 380 axially through the block 382 to a final position
where the adjusting screw end portion 394 is positioned within the socket
3~4.
By engaging the flats of the socket 384 with the flats of the
adjusting screw end portion 394, rotation of the hand wheel 378 in a
preselected direction is transmitted to the adjusting screw 338. The
slide block 332 together with the ~rive link end portion 362 are thus
moved laterally to a preselected posltion on the transfer arm 308 with
respect to the rotational axis 330 of the output shaft 302. Once the
- 32 -
:~7~?76
slide block 332 and the drive end portion 362 have been moved to a prese-
lected position on the transfer arm 308 corresponding to a preselected
feed length, the nut 36a is tightened on the threaded end 352.
The plate end portion 356 of the clamping bushing 354 is re-
turned to frictional engagenlent with the transEer arm 308 to retain the
drive link end portion 362 in the selected position on the transfer arm
308. This arrangement provides a very precise and easily obtained adjust-
ment in the feed length of the driven feed roll 16. The adjustment is
quickly accomplished avoiding downtime of the machine and eliminates the
need for maintaining a large inventory of gears which is required for
adjusting the feed length of the known material feed apparatus.
As further illustrated in Figures 8 and 9, the drive link second
end portion 364 is eccentrically connected adjacent to ~he periphery of
the gear 370, which is illustrated in Figure 9 as a gear segment having
gear teeth only on a radial segment 396 which is arranged to mesh with the
teeth of the gear 372. However, it should be understood that the gear to
which the drive link 334 is connected may have gear teeth around its
entire periphery. It should also be understood that the drive connection
of the drive link 334 to the driven feed roll 16 may include a plurality
of meshing gears, for example a set of four meshing gears as opposed to a
pair of meshing gears as in Figure 9.
The gear segment 370 is rotatably positioned on a gear shaft 398
by a bearing assembly 399. The gear shaft 398 is rotatably supported at
one end by a bracket 400 that is rigidly secured to the housing 12 and at
the opposite end to the housing-12. As seen in Figure 9, the point of
connection of the drive link second end portion 364 is horizontally
aligned with the axes of rotation of the gear shaft 398 and the feed roll
shaft end portion 374 which supports the other gear 372. The drive link
- 33 -
~ 7~
second end portion 364 is, in turn, connected eccentrically to the peri-
phery of the gear segment 370 ~y a pin 402. The drive link end portion
364 abuts the top surface of the gear segment 370 and is maintained in a
fixed axial position thereon by threaded engagement of a nut 404 with a
threaded end 406 of the pin 402. The pin 402 includes an opposite en-
larged end portion 408 that engages the under surface of gear segment
370. The gear segment 370 meshes with the gear 372 that is nonrotatably
connected to the shaft 374 of the driven feed roll 16.
The gear segment 370 is mounted in a similar manner as above
discussed for enlarged gear 90, shown in Figure 1, to facilitate the
movement of the gear 370 relative to the gear 372 to permit adjustments in
the meshing engagement of the gear teeth of gears 370 and 372. The gear
shaft 398 or. which the gear segment 370 is rotatably positioned includes
an eccentric end portion 410, illustrated in Figure 8. The eccentric end
portion 410 is positioned within a bore 412 of housing 12 and is retained
therein by a clamp ring 414. m e clamp ring 414 engages an enlarged
diameter portion 416 of the gear shaft 398. A pair of screws 418 engage
the clamp ring 414 to the housing 12. When the shaft eccentric end
portion 410 is clamped in position by the clamp ring 414, the eccentric
end portion 410 is nonrotatably retained in the bore 412 of the housing
12. However, by loosening the screws 418, the entire shaft 398 can be
rotated. .
As explained above with regard to the shaft 248 having the
eccentric end portion 250 illustrated in Figure 1, rotation of the shaft
398 permits the gear segment 370 to be moved laterally relative to the
gear 372 of the driven feed roll 16. This allows the gear teeth of the
gear segment 370 to be moved into and out of precise engagement with the
gear teeth of the gear 372. Thus, any backlash existing between the
meshing gears 370 and 372 can be renoved by first loosening the clamp
.
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1:17~t7~
ring 414 to permit rotation of the shaft 398 until the respective meshing
gear teeth are engaged in a manner ~`ree of hacklash. The gears 370 and
372 are then maintained in the deslred meshing position by securely
clamping the clamp ring 414 into engagement with the shaft enlarged
diameter portion 416 by tightening the screws 418. By remloving backlash
and play between the meshing gears 370 and 372, lost motion is removed in
the transmission of rotation from the linkage assembly 310 to the driven
feed roll 16.
As illustrated in Figure 8, the gear 372 that rotates the shaft
374 of the driven feed roll 16 is drivingly connected to the gear segment
370. However, as illustrated in Figure 9, it should be understood that
~he axis of rotation of the shaft 374 is positioned in the same horizontal
plane and parallel to the axis of the pin 402 that connects the drive link
334 to the gear segment 370. For purposes of clarity of illustration, in
Figure 8 the shaft 374 is shown displaced from its coplanar relationship
with the pin 402 in order to more clearly illustrate the transmission or
-rotation from the input shaft 280 to the output shaft 302 through the
linkage assembly 310 to the driven feed roll 16. Therefore, in Figure 8
the shaft 374 and the driven feed roll 16 are shown in a position lowered
from the Figure 9 position in the housing 12.
The shaft 374 is rotatably mounted at its opposite end portions
by a pair of bearing assemblies generally designated by the numerals 420
and 421 in the housing 12. The bearing assemblies 420 ar.d 421 are re-
tained in a preselected axial position on the shaft 374 by oombination
bearing nuts 422 and bearing washers 424. A mounting ring 426 and an
adapter 428 are secured to the housing 12 and retain the bearing assembly
421 in place on the end of the shaft-374 opposite the end of the shaft 374
that carries the gear 372. Thus with the above-described arrangement for
- - 35 -
the embodiment of the present invention illustrated in Figures ~ and 9,
the angular movement of the driven feed roll 16 is adjust2ble by adjusting
the position of the slide block 332 on the transfer arm 308 to, in turn,
adjust the length of travel of the drive link 334 and change the feed
length.
Now referring to Figures 12 and 13, there is illustrated an
adjustable material guide assembly generally designated by the numeral
426 for controlling the feeding of the stock materlal between the driven
feed roll 16 and the idler roll 17. The material guide asse~ly 426
is unted on the housing 12 between the feed roll 16 and the source
of stock material (not shown) that is fed by the feed roll 16 into the
press. m e stock material, for example, may include a continuous reel
of strip material having a preselected width and thickness and which is
to be selectively shaped and cut from the continuous web of the stock
material in preselected lengths or rewound after forming onto a continuous
reel. Also in acoordance with the present invention, the clamp cylinder
194 is secured on the housing 12 by the clc~mp support 200 in overlying
relation to the material guide assembly 426.
As illustrated in Figure 12, the material guide assembly 426
includes a movable material guide 428 and a stationary material guide
430. Preferably, the movable material guide 428 is a plate member which
is horizontally supported relative to the housing 12 for movement in a
vertical plane toward and away from the stationary material guide 430.
m e stationary material guide is also preferably a plate member which is
rigidly secured by means (not shcwn), such as by bolting to the housing
or machine frame 12. The stationary material guide 430 includes a bore
431 through which the rod 198 of the clamp cylinder 194 extends. The
pad 204 secured to the rod 198 is ~ertically movable relative to the
guide 430 into and out of clamping engagement with the stock material.
The pad 204 is shown in a clamped position in Figure 12.
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1~7~a~3!76
The stationary material guide 430 has a lower surface 432
which is positioned oppositely and in parallel relation with an upper
surface 434 of the movable material guide 428. The oppositely positioned
surfaces 432 and 434 are normally spaced a preselected vertical distance
apart to control and guide the movement of the stock material frGm the
source to the feed roll 16 and the idler roll 1?. The stock material is
freely movable between the overlying oppositely positioned surfaces 432
and 434, and as the material is pulled, as for example, from a reel and
fed in accordance with the present invention intermittently by the driven
feed roll 16 to the press.
The portion of the stock material advancing on the movable
material guide 428 toward the feed roll 16 is maintained along a substan-
tially linear feed path. The material guide assembly 426 prevents deflec-
tion of the stock material from a linear feed path to a sine curve feed
path. In accordance with the present invention, the relative position of
the movable material guide 428 to the stationary material guide 430 is
adjustable to acccmnodate a wide range of stock material thicknesses.
A support mechanism generally designated by the numeral 436 is
mounted on the machine frame 12 and supports the movable material guide
428 for movement to a preselected position spaced oppositely from the
stationary material guide 430. The support mechanism 436 is adjustable
to provide a preselected spacing of the movable material guide 430 from
the stationary material guide 428 so that the feed of stock material of
a preselected thickness is maintained along a substantially linear path
and is prevented from deflecting vertically from the feed path.
The support mechanism 436 includes a clamp devi oe generally
designated by the numeral 438 and an adjustment devioe generally desig-
nated by the numeral 440. The clamp device 438 is operable to secure
.
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~L~74~
the movable material guide 428 in a preselected position relative to the
stationary material guide 430 for feeding of a preselected thickness of
the stock material bet~een the oppositely positioned surfaces 432 and 434
along a substantially linear feed path. The adjustment device 440 sup-
ports the movable material guide 428 on the machine 12 for movement
toward and away from the stationary material guide 430. In this manner,
the vertical distance between the guides 428 and 430 is either increased
or decreased. The distance separating the plates 428 and 430 is thus
adjustable to accommcdate a wide range of stock material thicknesses.
As illustrated in Figure 12, the clamp device 438 includes
a post 442 that extends between the machine frame 12 and the movable
material guide 428. The post 442 includes a first end portion 444 seated
in the frame 12 and secured thereto by a screw 446. A second end portion
448 of the post 442 is removed from contact with the lower surface of the
mo~able material guide 428. A clamp 450 surrounds the post 442 and is
secured to the lower surface of the movable material guide 428 by a pair
of screws 452, only one of which is shcwn in Figure 12. The clamp 450
includes a bore 454 in which the post 442 is positioned. The clamp 450
is a bifurcated member that is movable into and out of frictional engage-
ment with the post 442.
When the clamp 450 is removed from frictional engagement with
the post 442, the clamp 450 and the movable guide plate 428 are movable
together as a unit relative to the fixed post 442 on the machine frame
12. Suitable means, such as a screw 456, extends through aligned threaded
bores of a pair of bifurcated sections 458 ~only one of which is shown
in Figure 12) of the clan~ 450. By loosening the screw 456 to remove the
clamp 450 from frictional engagement with the surface of the post 442, the
clamp is movable to a preselected position on the post 442. Acoordingly,
movement of the clamp 450 relative to.the fixed post 442 on the machine
frame 12 moves the movable material guide 428 vertically toward or away
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~ ~t7~
from the stationary material guicle 430. In this manner, the movable
material guide 428 is maintained in a preselected position relative
to the stationary material g~ide 430.
Tightening the screw 456 maintains the clamp 450 in a prese-
lected position on the post 442 where the end of the post opposite the
movable material guide 428 is maintained spaced fran contact with the
movable material guide 428. Thus, with the post 442 securely m~unted to
the machine frame 12 and the clan-~ 450 secured to the movable material
guide 428, tightening of the screw 456 to prevent relative movement
between the clamp 450 and the post 442 maintains the movable guide plate
428 at a preselected elevation above the machine frame 12 and spaced a
preselected distance from the stationary material guide 430.
The adjustment device 440 for controlling the distance between
the movable and stationary material guides 428 and 430 includes, as
illustrated in Figure 12 and in greater detail in Figure 13, a post 460
that extends between the machine frame 12 and the movable material guide
428. The post 460 includes a first end portion 462 seated in the machine
frame 12 and secured thereto by a screw 464. An enlarged second end
portion 466 is maintained removed from contact with the movable material
guide 428.
An adjustment member 468, such as a slide bloc~, is movable
in a .slot 470 of the machine frame 12. The slot 470 surrounds the post
460 and extends in a direction transversely to the direction of feed
of the stock material. The adjustment member 468 includes an elliptical
bore 472 through which the post 460 extends. m e elongated nature of
the bore 472 permits the adjustment member 468 to move transversely
relative to the post 460 through a given range on the machine frame 12.
The adjustment member 468 has a notched upper surface thereby forming
an inclined surface 474.
. - 39 -
7~ 7~
The adjustment clevice 440 also includes a slide member 476 that
coacts with the adjustmerlt member 46~. The slide member 476 includes an
enlarged upper end portion 478 that is suitably secured as by bolts 479 to
the movable material guide 428 and includes a lower end portion 480 having
an inclined surface 482 that slidably abuts the adjustment member inclined
surface 474 in surrounding relation with the elliptical bore 472. The
slide member 476 also has a bore 484 extending therethrough, and the bore
484 has an enlarged upper end portion 486 for receiving the enlarged
second end portion 466 of the post 460.
With this arrangement, the slide member 476 is movable on the
adjustment member inclined surface 474 upon release of the clamp 450 from
frictional engagement with the post 442. m e inclined surface 482 on the
slide member 476 is complimentary with the oppositely positioned inclined
surface 474 of the a3justment member 468. l'he slide member 476 is movable
upwardly and downwardly on the adjustment member inclined surface 474
within a range permitted by the length of the slot 472 in the adjustment
member 468.
As the adjustment member 468 moves, for example, to the left
in Figure 13, the slide member 476 advances up the inclined surface 474
to thereby raise the movable material guide 428 closer to the stationary
material guide 430. CorresFondingly, movement of the adjustment member
468 to the right advances the slide member 476 down the inclined surface
474 to lower the movable material guide 428 away from the stationary
material guide 430. Thus, by moving the adjustment member 468 in the
machine frame slot 470 in a preselected transverse direction, the ~.ovable
material guide 428 is moved either toward or away frc~ the stationary
material guide 430. In this manner, the spacing between the vable and
stationary material guides 428 and.430 is adjusted to permit passage of
stock material of a preselected thickness between the material guides 428
and 430 while preventing displace~ent of the stock material from the
surface of the movable material guide 428.
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76
When the selected spacing between the movable and stationary
material guides 428 and 430 is obtained for a preselected thickness of
the stock material, the clamp 450 is returned to frictional engagement
with the post 442 by tightening the screw 456 through the bifurcated
sections 458 of the clamp 450. In order to assure that the slide me~ber
476 is retained in a preselected position on the inclined surface 474
of the adjustment member 468, a resilient device, such as a compression
spring 488, is positioned within the enlarged diameter portion 486 of the
slide member bore 484 in surrounding relation with the post 460.
The compression spring 488 abuts at one end portion the post
enlarged second end portion 466 and at the opposite end a shoulder 490
of the slide member 476 positioned below the bore enlarged diameter
portion 486. The compression spring 488, with the post 460 rigidly
secured to the machine frame 12, normally exerts a downward force upon
the shoulder 490 and upon the slide member 476 to urge the slide member
inclined surface 482 into frictional engagement with the adjustment
member inclined surface 474. This arrangement maintains the slide member
476 in a preselected position after an adjustment is made on the adjust-
ment member 468 corresponding to a preselected thickness of the stoc~
material for passage between the movable and stationary material guides
428 and 430.
With the above-described arrangement of the material guide
asse~nbly 426, vertical deflection or sine-curve movement of the stock
~aterial to the driven feed roll 16 is prevented. In addition, a means
generally designated by the numeral 492 is provided on the movable mate-
rial guide 428 upstream of the:stationary material guide 430 for pre-
venting lateral deflection of the stock material in the plane of the feed
path as stock material is fed alc~ng the m vable material guide 42B. The
-- 41 --
~17~ 76
means 492 includes a pair of bars 494, only one of which i5 shcwn in
Figure 12, secured by bolts 496 in spaced parallel relation to the upper
surface of the movable material guide 428.
The pair of bars 494 are laterally spaced a distance apart
corresponding substantially to the width of the stock material fed to
driven feed roll 16. Each of the bars 494 is movable laterally toward
and away from each other to thereby decrease and increase the space
through which the stock material passes. The bars 494 also include
guide pins 498 that are movable in a transverse slot 500 extending across
the movable material guide 428 to maintain the bars 494 in spaced, para-
llel alignment. Preferably, each of the bars also includes a longitudinal
slot (not shown) through which the lateral edge of the stock material
is fed to further prevent lateral and vertical displacement of the stock
material on the movable material guide 428 as the material is fed into
engagement with the driven feed roll 16.
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