CA1170975A - Apparatus for intermittently clamping a workpiece - Google Patents
Apparatus for intermittently clamping a workpieceInfo
- Publication number
- CA1170975A CA1170975A CA000436624A CA436624A CA1170975A CA 1170975 A CA1170975 A CA 1170975A CA 000436624 A CA000436624 A CA 000436624A CA 436624 A CA436624 A CA 436624A CA 1170975 A CA1170975 A CA 1170975A
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- CA
- Canada
- Prior art keywords
- cam
- feed
- clamp
- rotation
- preselected
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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Landscapes
- Press Drives And Press Lines (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
An input shaft of a press feed is rotated at a preselected speed and is drivingly connected to a cam that rotates with the input shafts. Continuous rotation of the cam is converted to oscillating rotational movement of a cam follower through a preselected angle of rotation; The cam follower is nonrotatably connected to an output shaft that is connected by an adjustable linkage mechanism through a pair of meshing gears to a driven feed roll. The oscillating rotational movement of the output shaft is transmitted to the driven feed roll to advance the driven feed roll in contact with stock material through a preselected degree of rotation corresponding to a preselected feed length of the stock material to the press. A clamp is provided for intermittently engaging the workpiece to prevent movement thereof. The clamp is also cam driven through an air-actuated clamp cylinder.
An input shaft of a press feed is rotated at a preselected speed and is drivingly connected to a cam that rotates with the input shafts. Continuous rotation of the cam is converted to oscillating rotational movement of a cam follower through a preselected angle of rotation; The cam follower is nonrotatably connected to an output shaft that is connected by an adjustable linkage mechanism through a pair of meshing gears to a driven feed roll. The oscillating rotational movement of the output shaft is transmitted to the driven feed roll to advance the driven feed roll in contact with stock material through a preselected degree of rotation corresponding to a preselected feed length of the stock material to the press. A clamp is provided for intermittently engaging the workpiece to prevent movement thereof. The clamp is also cam driven through an air-actuated clamp cylinder.
Description
117~9';''5 This invention relates to apparatus for intermittently clamping a workpiece, specifically stock material fed intermittently to a press by oscillating rotationa] movement of a driven feed roll through a preselected angle of rotation.
This application is a divisional application of applicant's Canadian application Seria] 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 the 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. There-fore, 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.
~nited 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 punching operation is carried out. After the punching operation is completed, the feed rolls are again incrementally advanced so that another preselected mg/ . - 1 -9'75 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 eccentrlcally and is connected to a lever that is rotated to-and-fro. The pivotal movement of the lever is transmitted to a shaft thatis, 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 roIlers 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 inter-connecting the operations of feeding, clamping, and releasing the feed rolls that require many component parts which necessitate increased maintenance and replacement of worn parts.
mg/'c - 2 -1~7~975 The clamping apparatus of the present invention is used in conjunction with apparatus for intermittently feeding a workpiece that inc]udes 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. The 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 mg/J~ - 3 -117~75 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.
A 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.
During 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 the 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.
The 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 the arm member to provide a preselected angular displacement of the driven feed roll mg/`~
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 work-piece, the driven feed roll is moved into and out of feeding engagement with the workpiece, and in accordance with the present invention a clamping mechanism is moved into and out of clamping engagement with the workpiece during the dwell cycle. Thus, 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. The 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 mg/~,~ - 5 -1~7~9~5 driven feed roll to its initial position for feeding, the driven 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.
Specifically, the invention relates to apparatus for intermittently clamping a workpiece comprising, an input shaft supported for rotation at a continuous preselected speed, a linkage pivotally mounted at a first end relative to the input shaft, cam means nonrotatably connected to the input shaft for generating oscillating pivotal movement of the linkage, clamp means for intermittently engaging the workpiece to prevent movement of the workpiece, cylinder means having a rod extending from one end of the cylinder means, the clamp means being connected to the rod, support means for supporting the cylinder means for upward and downward reciprocal movement, the linkage being positioned in abutting relation at a second end to the cylinder means, the linkage being intermittently pivoted upwardly and downwardly upon rotation of the cam means to reciprocate the cylinder means upwardly and downwardly on the support means, and the clamp means being intermittently movable into and out of clamping engagement with the workpiece upon movement of the cylinder means.
~he 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.
mg/,. - 6 -1~7~975 Figure 2 is a fragmentary view taken along line II-II of Figure 1, illustrating a lir~age asser~bly that generates oscillating rotational r~vement of the feed roll thro~gh a preselected angle of rotation.
Figure 3 is a fragmentary, plan view, partially in section, of the cam drive connection of the feed press input shaft to an outpuL 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 synr chronously moving the feed and idler rolls, which are not shown in Figure 4, into and out of engagement with the workpiece, and clamping of the workpiece when the feed roll is released.
Figure 5 is a fragmentary view in side elevation taXen along line V-V of Figure 4, illustrating the linkages for actuating tshe ~pera-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 arrangem~nt for connecting a linkage asser~bly to the feed roll.
Figure 8 is a developed partial sectional view in side eleva-tion of a second er~bodiment of the cam feed apparatus, illustrating the input and output shafts positioned in parallel relation.
Figure 9 is a view taken along line IX-IX of Figure 8, illus-trating the drive connection to the input sshaft, and a handwheel for turning the adjusting screw tbat controls the position of the drive link on the transfer arm.
Figure 10 is a fragmentary view in side elevation of the c~m and cam follower arrangement for transmitting oscillatory motion to the output shaft of the cam feed sh~n in Figure 8.
1~7~75 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 adjustable 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 ad~usting the elevation of the top 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 by the numeral 10 for feeding a workpieoe such as continuous stock mat~-rial from a reel to a power operated press, as for example a press for stamping, punching, cutting or the like, of a preselected length of mate-rial frcm the workpiece. The 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. lhe 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. m e driven feed roll 16 and an idler roll 17 are operable, as will be explained later in greater detaiI; 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 overlying relation with the stock material caught between the feed and idler rolls.
D97~i The rotary m~tion of the input shaft 14 is converted by the cam feed mechanism 18 to generate noncontinuous, intermittent, 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 shæ t 14. The cam 20 includes a cam track 21 that is arranged to receive a cam follower 22 that is secured adjacent to the periphery of a circular cam plate 24. The cam plate 24 is axially and ncnrotatably secured tc a first end 26 of an output shaft 28 that is rotatably supported by bearings 30 in a bearing housing 32. m e output shaft 28, as seen in Fiqure 3, is 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 yreater detail.
- The bearing housing 32 is secured to the housing 12 by bolts 34. m e output shaft 28 includes a second end 36. A suitable oil seal 38 is positioned between the output shaft seoond 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 rotation of the cam 20 is oonverted 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 follows the cam track 21 of the cam 20 during one revolution of the cam 1~7~975 20, the cam plate 24 rotates from an initial position through an angle of 60. The cam plate 24 stops during a first dwell period of rotation of the canl 20 and then res~mes 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 second dwell period of rotation of the cam 20. This is a mcdified sine curve-type cam feed which oompensates 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.
The 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.
- - The oscillating movement of the cam plate 24 is transmitted 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 second end 36 by dowel pins 43 and cap screws 45. The transfer arm 44 slidably supports a slide block 46 that is connected to a drive link generally designated 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.
m e 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 block 46 is mov~ble in the recessed portion 56 by rotation of an adjusting screw 50, shown in Figure 13.7~975
This application is a divisional application of applicant's Canadian application Seria] 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 the 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. There-fore, 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.
~nited 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 punching operation is carried out. After the punching operation is completed, the feed rolls are again incrementally advanced so that another preselected mg/ . - 1 -9'75 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 eccentrlcally and is connected to a lever that is rotated to-and-fro. The pivotal movement of the lever is transmitted to a shaft thatis, 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 roIlers 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 inter-connecting the operations of feeding, clamping, and releasing the feed rolls that require many component parts which necessitate increased maintenance and replacement of worn parts.
mg/'c - 2 -1~7~975 The clamping apparatus of the present invention is used in conjunction with apparatus for intermittently feeding a workpiece that inc]udes 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. The 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 mg/J~ - 3 -117~75 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.
A 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.
During 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 the 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.
The 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 the arm member to provide a preselected angular displacement of the driven feed roll mg/`~
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 work-piece, the driven feed roll is moved into and out of feeding engagement with the workpiece, and in accordance with the present invention a clamping mechanism is moved into and out of clamping engagement with the workpiece during the dwell cycle. Thus, 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. The 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 mg/~,~ - 5 -1~7~9~5 driven feed roll to its initial position for feeding, the driven 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.
Specifically, the invention relates to apparatus for intermittently clamping a workpiece comprising, an input shaft supported for rotation at a continuous preselected speed, a linkage pivotally mounted at a first end relative to the input shaft, cam means nonrotatably connected to the input shaft for generating oscillating pivotal movement of the linkage, clamp means for intermittently engaging the workpiece to prevent movement of the workpiece, cylinder means having a rod extending from one end of the cylinder means, the clamp means being connected to the rod, support means for supporting the cylinder means for upward and downward reciprocal movement, the linkage being positioned in abutting relation at a second end to the cylinder means, the linkage being intermittently pivoted upwardly and downwardly upon rotation of the cam means to reciprocate the cylinder means upwardly and downwardly on the support means, and the clamp means being intermittently movable into and out of clamping engagement with the workpiece upon movement of the cylinder means.
~he 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.
mg/,. - 6 -1~7~975 Figure 2 is a fragmentary view taken along line II-II of Figure 1, illustrating a lir~age asser~bly that generates oscillating rotational r~vement of the feed roll thro~gh a preselected angle of rotation.
Figure 3 is a fragmentary, plan view, partially in section, of the cam drive connection of the feed press input shaft to an outpuL 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 synr chronously moving the feed and idler rolls, which are not shown in Figure 4, into and out of engagement with the workpiece, and clamping of the workpiece when the feed roll is released.
Figure 5 is a fragmentary view in side elevation taXen along line V-V of Figure 4, illustrating the linkages for actuating tshe ~pera-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 arrangem~nt for connecting a linkage asser~bly to the feed roll.
Figure 8 is a developed partial sectional view in side eleva-tion of a second er~bodiment of the cam feed apparatus, illustrating the input and output shafts positioned in parallel relation.
Figure 9 is a view taken along line IX-IX of Figure 8, illus-trating the drive connection to the input sshaft, and a handwheel for turning the adjusting screw tbat controls the position of the drive link on the transfer arm.
Figure 10 is a fragmentary view in side elevation of the c~m and cam follower arrangement for transmitting oscillatory motion to the output shaft of the cam feed sh~n in Figure 8.
1~7~75 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 adjustable 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 ad~usting the elevation of the top 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 by the numeral 10 for feeding a workpieoe such as continuous stock mat~-rial from a reel to a power operated press, as for example a press for stamping, punching, cutting or the like, of a preselected length of mate-rial frcm the workpiece. The 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. lhe 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. m e driven feed roll 16 and an idler roll 17 are operable, as will be explained later in greater detaiI; 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 overlying relation with the stock material caught between the feed and idler rolls.
D97~i The rotary m~tion of the input shaft 14 is converted by the cam feed mechanism 18 to generate noncontinuous, intermittent, 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 shæ t 14. The cam 20 includes a cam track 21 that is arranged to receive a cam follower 22 that is secured adjacent to the periphery of a circular cam plate 24. The cam plate 24 is axially and ncnrotatably secured tc a first end 26 of an output shaft 28 that is rotatably supported by bearings 30 in a bearing housing 32. m e output shaft 28, as seen in Fiqure 3, is 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 yreater detail.
- The bearing housing 32 is secured to the housing 12 by bolts 34. m e output shaft 28 includes a second end 36. A suitable oil seal 38 is positioned between the output shaft seoond 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 rotation of the cam 20 is oonverted 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 follows the cam track 21 of the cam 20 during one revolution of the cam 1~7~975 20, the cam plate 24 rotates from an initial position through an angle of 60. The cam plate 24 stops during a first dwell period of rotation of the canl 20 and then res~mes 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 second dwell period of rotation of the cam 20. This is a mcdified sine curve-type cam feed which oompensates 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.
The 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.
- - The oscillating movement of the cam plate 24 is transmitted 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 second end 36 by dowel pins 43 and cap screws 45. The transfer arm 44 slidably supports a slide block 46 that is connected to a drive link generally designated 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.
m e 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 block 46 is mov~ble in the recessed portion 56 by rotation of an adjusting screw 50, shown in Figure 13.7~975
2, having end ~ortions 52 and 53. ~n~ rtion ';~ extends through aligne~
bores of a cover plate 58 and an end block 60. Cover plate S8 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 reoe ssed portion 56. In this manner, the slide block end portion 70 is moved 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 positioning 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 assembly 42 to provide a preselected degree of rotation of the driven feed roll 16 and, accordingly, provide a preselected feed length for a fixed angular rotation oE the output shaEt 2a.
:1~7~9~375 The slide block bifurcated end portion 70 includes a transverse bore 78 shcwn in Figure 1, that is aligned with a bore 8~ in end E~rtion 82 of drive link 48. A clevis pin 84 extends through the aligned bores 78 and 80. A set screw 86 (Fi~ure 2) extends through end portion 70 to engage a flat of clevis pin 84 to prevent pin 84 from 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 adja oent 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 ~6 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 supE~rts 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 spàced arm members 102 and 104 which are oonnected by suitable fasteners 106 (Figure 2) to the drive linX end portion 82. The arm ~.embers 102 and 104 are connected to the gear gO by a clevis pin 108 extendil~ 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 asserr~ly 116 retained in the aE~erture 114 of the gear 90.
The arm members 102 and 104 are spaced from the roller bearing assern`bly 116 by a thrust bearing 118. The clevis pin lOU is retained in the aligned bores 110 and 112 and roller bearing assembly 116 by a set screw 120 (Figure 2) that extends through arm ~ember 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.
1.
The enlarged ~ear 90 includes a plurality of apertures 125, in addition to aperture 114, that are positioned at a preselected radial distance from the axis of rotation of the gear shaft 92. The drive link 48 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 se~ment 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 frcn the driven feed roll 16. The driven feed roll 16 is suitably supportea for rotation in the hou5ing 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 feed 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 bacX toward the driven feed roll 1~ 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 ~ixed to a rota-table shaft (not shown) in a manner as disclosed in United States Patent
bores of a cover plate 58 and an end block 60. Cover plate S8 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 reoe ssed portion 56. In this manner, the slide block end portion 70 is moved 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 positioning 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 assembly 42 to provide a preselected degree of rotation of the driven feed roll 16 and, accordingly, provide a preselected feed length for a fixed angular rotation oE the output shaEt 2a.
:1~7~9~375 The slide block bifurcated end portion 70 includes a transverse bore 78 shcwn in Figure 1, that is aligned with a bore 8~ in end E~rtion 82 of drive link 48. A clevis pin 84 extends through the aligned bores 78 and 80. A set screw 86 (Fi~ure 2) extends through end portion 70 to engage a flat of clevis pin 84 to prevent pin 84 from 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 adja oent 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 ~6 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 supE~rts 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 spàced arm members 102 and 104 which are oonnected by suitable fasteners 106 (Figure 2) to the drive linX end portion 82. The arm ~.embers 102 and 104 are connected to the gear gO by a clevis pin 108 extendil~ 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 asserr~ly 116 retained in the aE~erture 114 of the gear 90.
The arm members 102 and 104 are spaced from the roller bearing assern`bly 116 by a thrust bearing 118. The clevis pin lOU is retained in the aligned bores 110 and 112 and roller bearing assembly 116 by a set screw 120 (Figure 2) that extends through arm ~ember 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.
1.
The enlarged ~ear 90 includes a plurality of apertures 125, in addition to aperture 114, that are positioned at a preselected radial distance from the axis of rotation of the gear shaft 92. The drive link 48 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 se~ment 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 frcn the driven feed roll 16. The driven feed roll 16 is suitably supportea for rotation in the hou5ing 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 feed 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 bacX toward the driven feed roll 1~ 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 ~ixed to a rota-table shaft (not shown) in a manner as disclosed in United States Patent
3,977,589. The rotatable shaft is journaled within a frame which is rotated about an axis to move the idler roll 17 toward and away from the driven feed roll 16~ The rotatable shaft and frame will not be described in detail for the present invention.
Where desired, the link2ge assembly 42 may be ~onnected 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 90 and 124 deleted.
Hcwever, by utilizing the meshing gears 90 and 124 to transmit the oscil-lating rotational movement to the driven feed roll 16, it is pcssible to rotate the driven feed roll 16 through an angle greater th2n the angle of rotation of the output shaft 28. This permits an increase in the feed length over a feed length which would resul, from rotating the driven feed roll 16 through an angle corresponding to the angle of rotation of the output shaft 28. ~ccordingly, 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 2dditional 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 arrange~len~, very accurate adjustments can be quickly made in the feed length without the time consuming operation of changing feed rolls of different diameters.
1~7'1~375 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 o rotation, a second dwell period occurs during which time the cla~ing mechanism 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.
l'he 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. I'he 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 Fig~re 3, so that the feeding of the stock material is synchronized with the enga~ement of the rolls 16 and 17 with the stock material and release of the clamping mechanism 130 from engagement with the stock material.
1~7~3~75 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 is possible to change the sec~uence of the clamp release and the roll release operations 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 operar tions, it is possible to change the material feed direction to push the stock material into or pull the stock material away from the press. As stated above, the cam 20 for controlling the feed of the stock material to the press is synchronized with the movement of the clamp release cam 134 and the roll release cam. Therefore~ the operation of feeding the stock !naterial can take place upon rotation of the ca~ plate 24 and output shaft 28 in either a clockwise direction or a counterclockwise direction.
Accordingly, the direction of rotation of the output shaft 28 to actuate feeding of the stock material to the press determines during which dwell periods the operations of clamp release and roll release take place.
The roll release cam is not shown, but it should be understccd it is s~nilar to the clamp release cam 134 and includes a perip~eral cam surface that supports a cam follower 136, as illustrated, connected to the end of a cam follower arm 138 by a nut ar.d bolt co~ination 139. The cam arm 138 is pivotally mounted on a pivot pin 140 secured by a set screw 14 in the bore of a lug 144 that is connected to a lift arm 146. The lift arm 146 is pivotally ~ounted on one end of a shaft 14~ that is retained in a bore of an upstanding support 150. The shaft 148 is connected at the opposite end to housing 12. The supFort 150 is secured by fasteners 152 to a ~ounting bracket 154. The mounting bracket 154 is, in turn, con-nected by fasteners 156 to a side rail 158 that is connected by fasteners 160 to a side plate 162 of housing 12.
~1'7~75 The lift arm 1~6, as illustrat~ in ~`igure 6, is connected at one end to a roll reLease screw 164 by 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 the aligned bores. As illustrated in Figure 5, the lower end of the roll release screw 164 is connected to actuator arms 170. The actuator arms 170 are connected 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,g77,589 and therefore will not ke described in detail. The idler roll 17 is suitably journaled in the frame 172 so that upon rotation of the frame 172 by vement of the actuator ar~s 170, the idler roll 17 moves toward and away from the driven feed roll 16.
As illustrated in ~igure 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 clamp the arms 138 and 146.
An adjusting screw 178 extends through the end of the lift arm 146 and abuts the end of the cam follower arm 138 to adjustably position the cam follower arm 138 and cam follcwer 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 follcwer 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 the actuator arms 170.
During each cycle of the punch press; the actuator arms 170 are actuated to raise the frame 172 and thereby rotate the frame 172 to lcwer the idler rol] 17 away from the driven feed roll 16. This operation is disclosed in .
~7~3~7~
greater detail in the above-referenced United 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 Figure 5.
When the idler roll 17 is lowered, the stock material is dis-engaged from the rolls 16 and 17 so that the stock material is not fed to the punch press during the punching operation. Eurthermore, 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 17~ is rotated to raise the idler roll 17 toward the drive feed roll 16 to return the rolls 16 and 17 to driving engagement with t~e 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 clan~ing mechanism 130 is actuated by movement of a cam follower 180 on a cam surface 182 of the clamp release cam 134. The cam follower 180 is secured intermediate to a cam arm 184 by a nut and bolt combination 186. The cam arm 184 is pivotally mounted at one end p~rtion on the shaft 148. The opposite end of the cam arm 184 is provided with an adjusting screw 188 that extends through and below the cam arm 184. The adjusting screw 188 is secured in a selected position on the cam arm 184 by a nut 190.
The lower end of the adjusting screw 188, as illustrated in Figure 4, abuts the top surface of a pressure pad 192. The pressure pad 192 is suitably secured to an air actuated clamp cylinder 194. The claT~p :1~7~9~5 cylinder 1~4 is positioned for vertical n~vement in a ~ore 19~ of the mounting bracket 154. The cylinder 194 includes an extensible cylinder rod 198 that ex.ends belcw a clamp support 200 which reclines the lower end of clamp cylinder 194. The clanlp support 200 is positiorled for vertical movement below the mounting bracket 154. A set screw 202 ex-tends through the clamp support 200 and into engagement with the lower end portion of the clamp cylinder 194. Thus the clamp cylinder 194 is connected to the clamp support 200~ The cylinder rod 198 is connected by threaded engagement with a pad 2~4 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 shcwn in Figures 4 and 5.
The stock material 206 is supported for longitudinal vement on the surface 210 of a guide plate 212, as illustrated in Figures 4 and 5. The guide plate 212 is horizontall~ supported by a frame generally designated by the numeral 214. The frame 214 includes palrs of support members 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.
m e 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 206, the ~aterial 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 cylinder 194 in response to the pressure exerted on the pressure pad 192 by downward vement of the adjusting screw 188. The adjusting screw 188 moves downwardly by downward pivoting ~7~'~39~75 of the cam arm 1~4 on the shaft 148 as the cam follower 180 follcws the cam surface 182 of the rotating clamp release cam 134. By the application of dGwnward pressure upon the pressure pad 19~, the clamp cylinder 194 and the clamp support 200 are moved downwardly relative to the fixed mounting bracket 154. The clamp cylinder 194 is connected by conventional means (not shown) to a source of air under pressure. In this manner, the air pressure in the clamp 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 material 206.
A spring return mechanism generally designated 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 ypon continued rotation of the clamp release cam 134. This operation is synchronized with comrnencement 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 engagemRnt with the clamp support 200. The bolts 230 are each provided with an enlarged head 232 r 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 kolts 230 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 move~Rnt in the bushing 228 o the mounting bracket 154.
With this arrangement, upon release of pressure upon the clamp cylinder 194 by upward pivoting of the cam arm 184, the clamp cylinder 194 noves upwardly within the bore 196 of the mounting bracket 15~. 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 t~ 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 clamp support 200 moves upward with the bolts 230 upon extension of the coil springs 236. In this manner, the extended cylinder rod 198 is raised with the clamp cylinder 194 to remove the pad 204 from claT~ping engagement with the stock material 206. This permits unimpeded movement of the stoc~ material on the gui~e plate surface 210 during the feed cycle of the punch press.
The bolts 230 are vertically movable in the bushings 228 o~ the mounting bracket 154 which remains stationary. m e clamp support 200 is movable relative to the mounting braclcet 154. As illustrated i~ Figures
Where desired, the link2ge assembly 42 may be ~onnected 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 90 and 124 deleted.
Hcwever, by utilizing the meshing gears 90 and 124 to transmit the oscil-lating rotational movement to the driven feed roll 16, it is pcssible to rotate the driven feed roll 16 through an angle greater th2n the angle of rotation of the output shaft 28. This permits an increase in the feed length over a feed length which would resul, from rotating the driven feed roll 16 through an angle corresponding to the angle of rotation of the output shaft 28. ~ccordingly, 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 2dditional 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 arrange~len~, very accurate adjustments can be quickly made in the feed length without the time consuming operation of changing feed rolls of different diameters.
1~7'1~375 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 o rotation, a second dwell period occurs during which time the cla~ing mechanism 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.
l'he 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. I'he 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 Fig~re 3, so that the feeding of the stock material is synchronized with the enga~ement of the rolls 16 and 17 with the stock material and release of the clamping mechanism 130 from engagement with the stock material.
1~7~3~75 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 is possible to change the sec~uence of the clamp release and the roll release operations 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 operar tions, it is possible to change the material feed direction to push the stock material into or pull the stock material away from the press. As stated above, the cam 20 for controlling the feed of the stock material to the press is synchronized with the movement of the clamp release cam 134 and the roll release cam. Therefore~ the operation of feeding the stock !naterial can take place upon rotation of the ca~ plate 24 and output shaft 28 in either a clockwise direction or a counterclockwise direction.
Accordingly, the direction of rotation of the output shaft 28 to actuate feeding of the stock material to the press determines during which dwell periods the operations of clamp release and roll release take place.
The roll release cam is not shown, but it should be understccd it is s~nilar to the clamp release cam 134 and includes a perip~eral cam surface that supports a cam follower 136, as illustrated, connected to the end of a cam follower arm 138 by a nut ar.d bolt co~ination 139. The cam arm 138 is pivotally mounted on a pivot pin 140 secured by a set screw 14 in the bore of a lug 144 that is connected to a lift arm 146. The lift arm 146 is pivotally ~ounted on one end of a shaft 14~ that is retained in a bore of an upstanding support 150. The shaft 148 is connected at the opposite end to housing 12. The supFort 150 is secured by fasteners 152 to a ~ounting bracket 154. The mounting bracket 154 is, in turn, con-nected by fasteners 156 to a side rail 158 that is connected by fasteners 160 to a side plate 162 of housing 12.
~1'7~75 The lift arm 1~6, as illustrat~ in ~`igure 6, is connected at one end to a roll reLease screw 164 by 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 the aligned bores. As illustrated in Figure 5, the lower end of the roll release screw 164 is connected to actuator arms 170. The actuator arms 170 are connected 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,g77,589 and therefore will not ke described in detail. The idler roll 17 is suitably journaled in the frame 172 so that upon rotation of the frame 172 by vement of the actuator ar~s 170, the idler roll 17 moves toward and away from the driven feed roll 16.
As illustrated in ~igure 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 clamp the arms 138 and 146.
An adjusting screw 178 extends through the end of the lift arm 146 and abuts the end of the cam follower arm 138 to adjustably position the cam follower arm 138 and cam follcwer 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 follcwer 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 the actuator arms 170.
During each cycle of the punch press; the actuator arms 170 are actuated to raise the frame 172 and thereby rotate the frame 172 to lcwer the idler rol] 17 away from the driven feed roll 16. This operation is disclosed in .
~7~3~7~
greater detail in the above-referenced United 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 Figure 5.
When the idler roll 17 is lowered, the stock material is dis-engaged from the rolls 16 and 17 so that the stock material is not fed to the punch press during the punching operation. Eurthermore, 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 17~ is rotated to raise the idler roll 17 toward the drive feed roll 16 to return the rolls 16 and 17 to driving engagement with t~e 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 clan~ing mechanism 130 is actuated by movement of a cam follower 180 on a cam surface 182 of the clamp release cam 134. The cam follower 180 is secured intermediate to a cam arm 184 by a nut and bolt combination 186. The cam arm 184 is pivotally mounted at one end p~rtion on the shaft 148. The opposite end of the cam arm 184 is provided with an adjusting screw 188 that extends through and below the cam arm 184. The adjusting screw 188 is secured in a selected position on the cam arm 184 by a nut 190.
The lower end of the adjusting screw 188, as illustrated in Figure 4, abuts the top surface of a pressure pad 192. The pressure pad 192 is suitably secured to an air actuated clamp cylinder 194. The claT~p :1~7~9~5 cylinder 1~4 is positioned for vertical n~vement in a ~ore 19~ of the mounting bracket 154. The cylinder 194 includes an extensible cylinder rod 198 that ex.ends belcw a clamp support 200 which reclines the lower end of clamp cylinder 194. The clanlp support 200 is positiorled for vertical movement below the mounting bracket 154. A set screw 202 ex-tends through the clamp support 200 and into engagement with the lower end portion of the clamp cylinder 194. Thus the clamp cylinder 194 is connected to the clamp support 200~ The cylinder rod 198 is connected by threaded engagement with a pad 2~4 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 shcwn in Figures 4 and 5.
The stock material 206 is supported for longitudinal vement on the surface 210 of a guide plate 212, as illustrated in Figures 4 and 5. The guide plate 212 is horizontall~ supported by a frame generally designated by the numeral 214. The frame 214 includes palrs of support members 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.
m e 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 206, the ~aterial 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 cylinder 194 in response to the pressure exerted on the pressure pad 192 by downward vement of the adjusting screw 188. The adjusting screw 188 moves downwardly by downward pivoting ~7~'~39~75 of the cam arm 1~4 on the shaft 148 as the cam follower 180 follcws the cam surface 182 of the rotating clamp release cam 134. By the application of dGwnward pressure upon the pressure pad 19~, the clamp cylinder 194 and the clamp support 200 are moved downwardly relative to the fixed mounting bracket 154. The clamp cylinder 194 is connected by conventional means (not shown) to a source of air under pressure. In this manner, the air pressure in the clamp 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 material 206.
A spring return mechanism generally designated 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 ypon continued rotation of the clamp release cam 134. This operation is synchronized with comrnencement 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 engagemRnt with the clamp support 200. The bolts 230 are each provided with an enlarged head 232 r 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 kolts 230 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 move~Rnt in the bushing 228 o the mounting bracket 154.
With this arrangement, upon release of pressure upon the clamp cylinder 194 by upward pivoting of the cam arm 184, the clamp cylinder 194 noves upwardly within the bore 196 of the mounting bracket 15~. 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 t~ 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 clamp support 200 moves upward with the bolts 230 upon extension of the coil springs 236. In this manner, the extended cylinder rod 198 is raised with the clamp cylinder 194 to remove the pad 204 from claT~ping engagement with the stock material 206. This permits unimpeded movement of the stoc~ material on the gui~e plate surface 210 during the feed cycle of the punch press.
The bolts 230 are vertically movable in the bushings 228 o~ the mounting bracket 154 which remains stationary. m e clamp support 200 is movable relative to the mounting braclcet 154. As illustrated i~ 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 between 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 and 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 clamp 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 claTTIp cylinder 194.
The cylinder 194 moves downwardiy within the bore 196 of the mounting bracket 154 and compresses the coil springs 236. As described above, 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 1~7~g~75 directed u~on the upper end of the cylinder rod 198. When the cylinder 194 and the rod 198 m.ove downwardly, the pad 204 is n~ved into clampiny engagement with the stock material 206. During the clamping engagement of the stock material, the air in the clamp cylinder 194 is further com-pressed to assure that the pad 204 exerts a preselected pressure upon the stock material 206 to prevent it fran n~ving on the guide plate surface 210. Thus, the stock material 206 is not advanced backwardly during the cycle when the feed roll 1~ 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. The 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 surface 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 stock material and clamping the stock material are coordinated with the oscilla-ting rotational movement of the output shaft 28 by the cam feed ~,echanism 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 portion 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 1~7~75 the enlarged diameter portion 254 and the shaft b~dy portion 248 are concentric, while the axis of the stub end portion 250 is eccentric relative.to the axes of shaft portions 24~ ana 2~4.
The shaft stub end portion 250 is held within the bore 252 by the clamp ring 96 engaging the enlargéd diameter portion 254 and the cap screw 94 threaded tightly into engagement with the clamp ring 96 and the housing 12. When the stub end portion 250 is cla ~ in position by the clamp 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 tee~.h 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 clamp ring 96 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 enlarged gear 90 in order to c~mpensate 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.
1~7~D97~
The ability to adjust the position o~ the enlarged gear 90 obviates the need for precise machining of the clrive gears so that toler-ances may be permitted within the range of adjustment that can be made.
This 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 ro~ation free of lost motion 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 shcwn in Figures 1 and 2 for transmitting rotation fr~m the linkage mechanism 42 through a gear train of two or more gears to the driven feed roll 16. The feed length for the embodiment of Figure 7 is also adjusted by moving the slide block 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 incl~des a drive link generally designated ~y 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 2~0 is, in turn, connected to a secondary link 264 by a suitable connector 266 extending through aligned bores in the second link portion 260 and the secondary link 264. The secondary linX 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.
1~7rJ)~
In this manner, the driven feed roll 16 is rotated 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, I
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 corresFond to the similar features illustrated in Figures 1-7 and discussed above in detail.
In the second embodiment 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 pcwered input shaft 280, which is illustrated in dotted lines in Figure 9 and m 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 ~83, shcwn in Figure 9. Gear 282 is nonrotatably connected to the intermediate 117~975 portion of the first input shaft ~70, and gear 283 is nonrotatably connec-ted to a first end portion 284 of the second input shaft 280. The second powered input shaft 280 is also rotatably supported in the machine housing 12 by conventional bearing assemblies generally designated by the nu~Rrals 286 and 288. The 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 embodiment of the intermittent feed apparatus 10 also includes a material clamping mechanism generally designated by the numeral 292 and a feed release mechani~m generally designated by the numeral 294. The respective mechanisms 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 292 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 describèd for the cla~ping mechanism 130 and the feed release mechanism 132. Therefore, these operations will not be discussed in greater detail for the second ~mbodiment of the intermittent feed apparatus 10.
1~7~D9~;~5 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 designated by the numeral 300 to oscillating 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 in spaced parallel relation to the second 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 norrotatably connected by a plurality 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 yoke members 320 and 322, respectively. The cams 312 and 314 have a preselected configuration to ccnvert the continuous rotation of the second input shaft 280 to oscillating rotational move~ent 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.
117~975 Each of the cam followers 316 and 318 is mounted on a pin 328 which is rotatably retained in the respective yoke members 320 and 322 to permit rotation of the cam followers 316 and 318 as the cam followers 316 and 318 move on the peripheral surfaces of the cams 312 and 314.
As illustrated in Figure 10, the yoke members 320 and 322 maintain the cam followers 316 and 318 in contact with the peripheral surfaces of the cams 312 and 314. Each of the c~ns 312 and 314 has a corresponding configuration to generate oscillating rotational m~vement 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 embodiment ilustrated in Figure 1, as the cam followers 316 and 318 follow 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 preselectèd angle, as for example, an angle of 60.
The yoke members 320 and 322 and the output shaft 302 stop during a first dwell pericd of rotation of the c~ns 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 providing a pair of cams 312 and 314, the inertia of the moving stock material generated by acceleration of the stock material from an initial rest position to a maximum feed rate and then deceleratlng the stock material from the maximum feed 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. .
1~'7~9'75 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 foll~wers 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 15. ~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 nu~eral 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.
m e transfer arm 308 has a longitudinally extending recessed portion 340 aligned with the adjusting screw axis 336. The slide block 332 is longitudinally vable 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 re oeiving the adjusting screw 338. As seen in Figure 9, the adjusting screw 338 is rotatably supported at its end portions in bearing blocXs 346 and 348 which are secured to the transfer arm 308. With this arrangement, the adjusting screw 338 is rotatable relative to the transfer arm 3~8 but is 1.
~'7~7S
restrained from axial n~ovement relative to the transfer arm 308. Upon rotation of the adjusting screw 338 in a preselect~d airection, the slide block 332 ves longitudinally in the recessed portion 340 to a prese-lected position on the transfer arm 308.
A shaft 350 having a threaded end 352 is fo~r.ed integral with the slide block 332 and extends outwardly therefrom. A clamp bushing 354 is positioned on the shaft 350. The clamp hushing 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 block 332 where the recessed portion 358 extends the length of the recessed portion 340.
A shaft portion 360 extends from 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 engagem~ent 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. Hcwever, 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 -- .~0 117~3975 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 ve-ment of the output shaft 302 is transmitted to the driven feed roll 16 to thereby rotate the driven feed roll 16 through a preselected angle cor-responding to a preselected length of the workpiece to be fed to a press.
The length of travel of the drive link 334 generated by the oscillating rotational movement of the output shaft 302 is adjustable, I
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 accordingly the degree of rotation of the driven feed roll 16 and the resultant feed len~th 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. I
Accordingly, to reduce the feed length, the drive link first end portion 362 is ved 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 and 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 clamp bushing plate end portion 356 frcm 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 ~7~975 loaded actuating device generally designated by the numeral 376 in Figure 9. The actuating device 376 includes a hand wheel 378 nonrotatably connected 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 opposite 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 compression spring 390.
m e spring 390 abuts at one end against a bearing sleeve 392 through which the shaft 380 extends 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 accomplished 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, the spring 390 is comr 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 384.
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 position on the transfer arm 308 with respect to the rotational axis ~30 of the output shaft 302. On oe the !3g75 slide block 332 and the drive end portion 362 have been moved to a prese-lected position on the transfer arm 3U8 corresponding to a preselected feed length, the nut 368 is tightened on the threaded end 352.
The plate end portion 356 of the clamping bushing 354 is re-turned to frictional engagement with the transfer 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 adjust~ent 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 kncwn material feed apparatus.
As further illustrated in Figures 8 and 9, the drive link second end portion 364 is eccentrically connected adjacent to the periphery of the gear 370, which is illustrated in Figure 9 as a gear segment havin~
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 37D 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 l2. 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 second end portion 364 is, in turn, c~nnected eccentrically to the peri-phery of the gear segment 370 by 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 surfaoe 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 engagemRnt of the gear teeth of gears 370 and 372. The gear shaft 398 on which the gear seg~Rnt 370 is rotatably positioned includes an eccentric end portion 410, illustrated in Figure 8. The eccentric end portion 410 is ~ositioned within a bore 412 of housiny 12 and is retained therein by a clamp ring 414. The 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 loosenin~ 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 removed by first loosening the clamp - 3~ -11~713~75 ring 41~1 to permit rotation of the shaft 398 until the respective meshing gear teeth are engaged in a manner free of backlash. The gears 370 and 372 are then maintained in the clesired meshing position by securely clamping the clamp ring 414 into engagement with the shaft enlarged diameter portion 416 by tightening the screws 418. By removing 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 1 370. However, as illustrated in Figure 9, it should be understood that the 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. m e bearing assemblies 420 ard 421 are re-tained in a preselected axial position on the shaft 374 by combination bearing nuts 422 and bearing washers 424. A mounting ring 426 and an adapter 428 are secured to the housing 12 and retain t~e bearing assembly 421 in place on the end of the shaft 374 opposite the end of the shaft 374 that carries the gear 372. m us with the above-described arrangement for the embcdiment of the present invention illustrated in Figures 8 and 9, the angular movement of the driven feed roll 16 is adjustable 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 material between the driven feed roll 16 and the idler roll 17. The material guide assembly 426 is mounted on the housing 12 between the feed roll 16 and the source of stock material (not sh~n) that lS fed by the feed roll 16 into the press. The stock material, for example, may include a continuous reel of strip material having a preselected width and thickness and which is to be selectively shap~d and cut frQm the continuous web of the stock material in preselected lengths or rewound after forming onto a continuous reel. Also in accordance with the present invention, the clamp cylinder 194 is secured on the housing 12 by the clamp 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. lhe pad 204 secured to the rod 198 is vertically 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.
117~ 75 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 17. The stock material is freely vable 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 accordarce with the present invention, the relative position of the movable material guide 428 to the stationary material guide 430 is adjustable to accommodate a wide range of stock ~terial 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 fro~ 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 frcm the feed path.
The support mechanism 436 includes a clamp device gene~ally designated by the numeral 438 and an adjustment device generally desig-nated by the numeral 440. The clamp device 438 is operable to secure ~L7~D~7S
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 between the oppositely positioned surfaces 432 and 434 along a substantially linear feed path. The adjustment devioe 44~ sup-ports the movable material guide 428 on the machine 12 for movement tc~ard 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 accommodate 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 movable 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 shGwn 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 frc~ 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 clamp 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. Accordingly, 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 fro~ the stationary material guide 430. In this manner, the movable material guide 428 is maintained in a preselected position relative to the stationary material guide 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 from contact with the movable material quide 428. Thus, with the post 442 securely ~ounted to the machine frame 12 and the clanlp 450 secured tc 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 frorn 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 block, 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. The 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.
m e adjustment me~ber 468 has a notched upper surface thereby forming an inclined surface 474.
. - 39 -~7~3975 The adj~stment clevice 440 also includes a slide mem~er 476 that coacts with the adjustment member 468. 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. The inclined surface 482 on the slide member 476 is complimentary with the oppositely positioned inclined surface 474 of the adjustment member 468. The slide member 476 is inovable 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. Correspondingly, move~ent of the adiustment 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 458 in the machine frame slot 470 in a preselected transverse direction, the movable material guide 428 is moved either toward or away from the stationary material guide 430. In this manner, the spacing between the n~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 displacement of the stock material frcn the surface of the movable material guide 428.
1~7~D~75 ~ hen the selected spa~ing between the n;ovable and stationary material guides 428 and 430 is obtained for a preselected thickness of the stock material, the cl~ 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 mem~er 476 is retained in a preselected position on the inclined surfaoe 474 of the adjustment member 468, a resilient device, such as a compression spring 488, is positioned within the enlarg~d diameter portion 486 of the slide member bore 484 in surrounding relation ~ith the post 460.
m e 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 oorresponding to a preselected thickness of the stock material for passage between the movable and stationary material guides 428 and 430.
With the above-described arrangement of the material guide assembly 426, vertical deflection or sine-curve movement of the stock material 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 s~k raterial is ted along the movatle naterial guide 428. The ~3 7~9'75 means 492 includes a pair o~ bars 494, only one of which is s~lown 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 spaced9 parar 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 42B as the material is fed into engegement with the driv~n feed r 11 16.
.
During the period of roll release, the clamp 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 claTTIp cylinder 194.
The cylinder 194 moves downwardiy within the bore 196 of the mounting bracket 154 and compresses the coil springs 236. As described above, 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 1~7~g~75 directed u~on the upper end of the cylinder rod 198. When the cylinder 194 and the rod 198 m.ove downwardly, the pad 204 is n~ved into clampiny engagement with the stock material 206. During the clamping engagement of the stock material, the air in the clamp cylinder 194 is further com-pressed to assure that the pad 204 exerts a preselected pressure upon the stock material 206 to prevent it fran n~ving on the guide plate surface 210. Thus, the stock material 206 is not advanced backwardly during the cycle when the feed roll 1~ 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. The 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 surface 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 stock material and clamping the stock material are coordinated with the oscilla-ting rotational movement of the output shaft 28 by the cam feed ~,echanism 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 portion 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 1~7~75 the enlarged diameter portion 254 and the shaft b~dy portion 248 are concentric, while the axis of the stub end portion 250 is eccentric relative.to the axes of shaft portions 24~ ana 2~4.
The shaft stub end portion 250 is held within the bore 252 by the clamp ring 96 engaging the enlargéd diameter portion 254 and the cap screw 94 threaded tightly into engagement with the clamp ring 96 and the housing 12. When the stub end portion 250 is cla ~ in position by the clamp 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 tee~.h 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 clamp ring 96 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 enlarged gear 90 in order to c~mpensate 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.
1~7~D97~
The ability to adjust the position o~ the enlarged gear 90 obviates the need for precise machining of the clrive gears so that toler-ances may be permitted within the range of adjustment that can be made.
This 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 ro~ation free of lost motion 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 shcwn in Figures 1 and 2 for transmitting rotation fr~m the linkage mechanism 42 through a gear train of two or more gears to the driven feed roll 16. The feed length for the embodiment of Figure 7 is also adjusted by moving the slide block 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 incl~des a drive link generally designated ~y 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 2~0 is, in turn, connected to a secondary link 264 by a suitable connector 266 extending through aligned bores in the second link portion 260 and the secondary link 264. The secondary linX 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.
1~7rJ)~
In this manner, the driven feed roll 16 is rotated 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, I
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 corresFond to the similar features illustrated in Figures 1-7 and discussed above in detail.
In the second embodiment 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 pcwered input shaft 280, which is illustrated in dotted lines in Figure 9 and m 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 ~83, shcwn in Figure 9. Gear 282 is nonrotatably connected to the intermediate 117~975 portion of the first input shaft ~70, and gear 283 is nonrotatably connec-ted to a first end portion 284 of the second input shaft 280. The second powered input shaft 280 is also rotatably supported in the machine housing 12 by conventional bearing assemblies generally designated by the nu~Rrals 286 and 288. The 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 embodiment of the intermittent feed apparatus 10 also includes a material clamping mechanism generally designated by the numeral 292 and a feed release mechani~m generally designated by the numeral 294. The respective mechanisms 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 292 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 describèd for the cla~ping mechanism 130 and the feed release mechanism 132. Therefore, these operations will not be discussed in greater detail for the second ~mbodiment of the intermittent feed apparatus 10.
1~7~D9~;~5 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 designated by the numeral 300 to oscillating 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 in spaced parallel relation to the second 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 norrotatably connected by a plurality 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 yoke members 320 and 322, respectively. The cams 312 and 314 have a preselected configuration to ccnvert the continuous rotation of the second input shaft 280 to oscillating rotational move~ent 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.
117~975 Each of the cam followers 316 and 318 is mounted on a pin 328 which is rotatably retained in the respective yoke members 320 and 322 to permit rotation of the cam followers 316 and 318 as the cam followers 316 and 318 move on the peripheral surfaces of the cams 312 and 314.
As illustrated in Figure 10, the yoke members 320 and 322 maintain the cam followers 316 and 318 in contact with the peripheral surfaces of the cams 312 and 314. Each of the c~ns 312 and 314 has a corresponding configuration to generate oscillating rotational m~vement 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 embodiment ilustrated in Figure 1, as the cam followers 316 and 318 follow 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 preselectèd angle, as for example, an angle of 60.
The yoke members 320 and 322 and the output shaft 302 stop during a first dwell pericd of rotation of the c~ns 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 providing a pair of cams 312 and 314, the inertia of the moving stock material generated by acceleration of the stock material from an initial rest position to a maximum feed rate and then deceleratlng the stock material from the maximum feed 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. .
1~'7~9'75 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 foll~wers 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 15. ~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 nu~eral 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.
m e transfer arm 308 has a longitudinally extending recessed portion 340 aligned with the adjusting screw axis 336. The slide block 332 is longitudinally vable 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 re oeiving the adjusting screw 338. As seen in Figure 9, the adjusting screw 338 is rotatably supported at its end portions in bearing blocXs 346 and 348 which are secured to the transfer arm 308. With this arrangement, the adjusting screw 338 is rotatable relative to the transfer arm 3~8 but is 1.
~'7~7S
restrained from axial n~ovement relative to the transfer arm 308. Upon rotation of the adjusting screw 338 in a preselect~d airection, the slide block 332 ves longitudinally in the recessed portion 340 to a prese-lected position on the transfer arm 308.
A shaft 350 having a threaded end 352 is fo~r.ed integral with the slide block 332 and extends outwardly therefrom. A clamp bushing 354 is positioned on the shaft 350. The clamp hushing 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 block 332 where the recessed portion 358 extends the length of the recessed portion 340.
A shaft portion 360 extends from 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 engagem~ent 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. Hcwever, 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 -- .~0 117~3975 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 ve-ment of the output shaft 302 is transmitted to the driven feed roll 16 to thereby rotate the driven feed roll 16 through a preselected angle cor-responding to a preselected length of the workpiece to be fed to a press.
The length of travel of the drive link 334 generated by the oscillating rotational movement of the output shaft 302 is adjustable, I
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 accordingly the degree of rotation of the driven feed roll 16 and the resultant feed len~th 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. I
Accordingly, to reduce the feed length, the drive link first end portion 362 is ved 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 and 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 clamp bushing plate end portion 356 frcm 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 ~7~975 loaded actuating device generally designated by the numeral 376 in Figure 9. The actuating device 376 includes a hand wheel 378 nonrotatably connected 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 opposite 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 compression spring 390.
m e spring 390 abuts at one end against a bearing sleeve 392 through which the shaft 380 extends 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 accomplished 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, the spring 390 is comr 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 384.
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 position on the transfer arm 308 with respect to the rotational axis ~30 of the output shaft 302. On oe the !3g75 slide block 332 and the drive end portion 362 have been moved to a prese-lected position on the transfer arm 3U8 corresponding to a preselected feed length, the nut 368 is tightened on the threaded end 352.
The plate end portion 356 of the clamping bushing 354 is re-turned to frictional engagement with the transfer 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 adjust~ent 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 kncwn material feed apparatus.
As further illustrated in Figures 8 and 9, the drive link second end portion 364 is eccentrically connected adjacent to the periphery of the gear 370, which is illustrated in Figure 9 as a gear segment havin~
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 37D 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 l2. 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 second end portion 364 is, in turn, c~nnected eccentrically to the peri-phery of the gear segment 370 by 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 surfaoe 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 engagemRnt of the gear teeth of gears 370 and 372. The gear shaft 398 on which the gear seg~Rnt 370 is rotatably positioned includes an eccentric end portion 410, illustrated in Figure 8. The eccentric end portion 410 is ~ositioned within a bore 412 of housiny 12 and is retained therein by a clamp ring 414. The 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 loosenin~ 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 removed by first loosening the clamp - 3~ -11~713~75 ring 41~1 to permit rotation of the shaft 398 until the respective meshing gear teeth are engaged in a manner free of backlash. The gears 370 and 372 are then maintained in the clesired meshing position by securely clamping the clamp ring 414 into engagement with the shaft enlarged diameter portion 416 by tightening the screws 418. By removing 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 1 370. However, as illustrated in Figure 9, it should be understood that the 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. m e bearing assemblies 420 ard 421 are re-tained in a preselected axial position on the shaft 374 by combination bearing nuts 422 and bearing washers 424. A mounting ring 426 and an adapter 428 are secured to the housing 12 and retain t~e bearing assembly 421 in place on the end of the shaft 374 opposite the end of the shaft 374 that carries the gear 372. m us with the above-described arrangement for the embcdiment of the present invention illustrated in Figures 8 and 9, the angular movement of the driven feed roll 16 is adjustable 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 material between the driven feed roll 16 and the idler roll 17. The material guide assembly 426 is mounted on the housing 12 between the feed roll 16 and the source of stock material (not sh~n) that lS fed by the feed roll 16 into the press. The stock material, for example, may include a continuous reel of strip material having a preselected width and thickness and which is to be selectively shap~d and cut frQm the continuous web of the stock material in preselected lengths or rewound after forming onto a continuous reel. Also in accordance with the present invention, the clamp cylinder 194 is secured on the housing 12 by the clamp 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. lhe pad 204 secured to the rod 198 is vertically 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.
117~ 75 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 17. The stock material is freely vable 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 accordarce with the present invention, the relative position of the movable material guide 428 to the stationary material guide 430 is adjustable to accommodate a wide range of stock ~terial 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 fro~ 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 frcm the feed path.
The support mechanism 436 includes a clamp device gene~ally designated by the numeral 438 and an adjustment device generally desig-nated by the numeral 440. The clamp device 438 is operable to secure ~L7~D~7S
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 between the oppositely positioned surfaces 432 and 434 along a substantially linear feed path. The adjustment devioe 44~ sup-ports the movable material guide 428 on the machine 12 for movement tc~ard 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 accommodate 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 movable 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 shGwn 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 frc~ 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 clamp 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. Accordingly, 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 fro~ the stationary material guide 430. In this manner, the movable material guide 428 is maintained in a preselected position relative to the stationary material guide 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 from contact with the movable material quide 428. Thus, with the post 442 securely ~ounted to the machine frame 12 and the clanlp 450 secured tc 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 frorn 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 block, 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. The 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.
m e adjustment me~ber 468 has a notched upper surface thereby forming an inclined surface 474.
. - 39 -~7~3975 The adj~stment clevice 440 also includes a slide mem~er 476 that coacts with the adjustment member 468. 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. The inclined surface 482 on the slide member 476 is complimentary with the oppositely positioned inclined surface 474 of the adjustment member 468. The slide member 476 is inovable 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. Correspondingly, move~ent of the adiustment 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 458 in the machine frame slot 470 in a preselected transverse direction, the movable material guide 428 is moved either toward or away from the stationary material guide 430. In this manner, the spacing between the n~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 displacement of the stock material frcn the surface of the movable material guide 428.
1~7~D~75 ~ hen the selected spa~ing between the n;ovable and stationary material guides 428 and 430 is obtained for a preselected thickness of the stock material, the cl~ 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 mem~er 476 is retained in a preselected position on the inclined surfaoe 474 of the adjustment member 468, a resilient device, such as a compression spring 488, is positioned within the enlarg~d diameter portion 486 of the slide member bore 484 in surrounding relation ~ith the post 460.
m e 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 oorresponding to a preselected thickness of the stock material for passage between the movable and stationary material guides 428 and 430.
With the above-described arrangement of the material guide assembly 426, vertical deflection or sine-curve movement of the stock material 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 s~k raterial is ted along the movatle naterial guide 428. The ~3 7~9'75 means 492 includes a pair o~ bars 494, only one of which is s~lown 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 spaced9 parar 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 42B as the material is fed into engegement with the driv~n feed r 11 16.
.
Claims
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Apparatus for intermittently clamping a workpiece comprising, an input shaft supported for rotation at a continu-ous preselected speed, a linkage pivotally mounted at a first end relative to said input shaft, cam means nonrotatably connected to said input shaft for generating oscillating pivotal movement of said linkage, clamp means for intermit-tently engaging the workpiece to prevent movement of the workpiece, cylinder means having a rod extending from one end of said cylinder means, said clamp means being connected to said rod, support means for supporting said cylinder means for upward and downward reciprocal movement, said linkage being positioned in abutting relation at a second end to said cylin-der means, said linkage being intermittently pivoted upwardly and downwardly upon rotation of said cam means to reciprocate said cylinder means upwardly and downwardly on said support means, and said clamp means being intermittently movable into and out of clamping engagement with the workpiece upon movement of said cylinder means.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA000436624A CA1170975A (en) | 1980-01-14 | 1983-09-13 | Apparatus for intermittently clamping a workpiece |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11206680A | 1980-01-14 | 1980-01-14 | |
US112,066 | 1980-01-14 | ||
US182,463 | 1980-08-28 | ||
US06/182,463 US4316569A (en) | 1980-01-14 | 1980-08-28 | Oscillating cam feed apparatus for a press |
CA000368301A CA1159764A (en) | 1980-01-14 | 1981-01-12 | Oscillating cam feed apparatus for a press |
CA000436624A CA1170975A (en) | 1980-01-14 | 1983-09-13 | Apparatus for intermittently clamping a workpiece |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CA000368301A Division CA1159764A (en) | 1980-01-14 | 1981-01-12 | Oscillating cam feed apparatus for a press |
Publications (1)
Publication Number | Publication Date |
---|---|
CA1170975A true CA1170975A (en) | 1984-07-17 |
Family
ID=27426285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CA000436624A Expired CA1170975A (en) | 1980-01-14 | 1983-09-13 | Apparatus for intermittently clamping a workpiece |
Country Status (1)
Country | Link |
---|---|
CA (1) | CA1170975A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107457696A (en) * | 2017-09-21 | 2017-12-12 | 上海应用技术大学 | A kind of frock clamp |
CN109809236A (en) * | 2019-04-03 | 2019-05-28 | 广州市兴世机械制造有限公司 | The box winding device of band storing |
-
1983
- 1983-09-13 CA CA000436624A patent/CA1170975A/en not_active Expired
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107457696A (en) * | 2017-09-21 | 2017-12-12 | 上海应用技术大学 | A kind of frock clamp |
CN107457696B (en) * | 2017-09-21 | 2023-03-21 | 上海应用技术大学 | Work fixture |
CN109809236A (en) * | 2019-04-03 | 2019-05-28 | 广州市兴世机械制造有限公司 | The box winding device of band storing |
CN109809236B (en) * | 2019-04-03 | 2024-02-09 | 广州市兴世机械制造有限公司 | Box rolling equipment for strip storage |
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