US3620381A - Horizontal high-speed transfer - Google Patents

Horizontal high-speed transfer Download PDF

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US3620381A
US3620381A US25725A US3620381DA US3620381A US 3620381 A US3620381 A US 3620381A US 25725 A US25725 A US 25725A US 3620381D A US3620381D A US 3620381DA US 3620381 A US3620381 A US 3620381A
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cam
carrier
bar
slide
cam bar
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Stuart H Mccaughey
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02Advancing work in relation to the stroke of the die or tool
    • B21D43/04Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/05Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work specially adapted for multi-stage presses
    • B21D43/055Devices comprising a pair of longitudinally and laterally movable parallel transfer bars
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B65CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65GTRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G25/00Conveyors comprising a cyclically-moving, e.g. reciprocating, carrier or impeller which is disengaged from the load during the return part of its movement
    • B65G25/02Conveyors comprising a cyclically-moving, e.g. reciprocating, carrier or impeller which is disengaged from the load during the return part of its movement the carrier or impeller having different forward and return paths of movement, e.g. walking beam conveyors

Definitions

  • the carrier bars are positively connected to the cam bars for lateral in and out movement therewith and for relative sliding.
  • the carrier supports and cam bars are independently reciprocated in phase displaced relationship so the carrier bar moves forward after the cam bar has moved inward, and so the cam bar draws the carrier outward before the carrier is returned to its first position.
  • the carrier and cam bar are reciprocated by separate rotating cams and followers.
  • a cam flange extends radially outward from a cylindrical body and followers are mounted on opposite sides of the flange for continuous uniform direction rotation of the followers as the cam rotates, and the followers move slides which are connected to the cam bar and carrier bar.
  • Very high-speed press operations are made possible by new tool materials and press designs.
  • One area which has limited the speed of press operations is the transfer apparatus which is used to feed articles from station to station in presses.
  • Article feed or transfer apparatus has heretofore employed springs which required excessive operational times to move a part from one position to another.
  • workpieces which are not well engaged and held tend to float and misalign, jamming the machinery, or causing high-rejection rates, and necessitating high percentages of inspection and sampling. Forces which cause floating and misalignment increase geometrically with increasing cyclic speeds.
  • Movements must be very accurate in all transfers. In highspeed transfers, the accuracy of the transfer movements becomes critical. Play or backlash in transfer apparatus causes many problems which cannot be tolerated in high-speed equipment. Because of the increased accelerations, many conditions which are completely workable at low speeds, become destructive at high speeds. For example, the periodic reversing of direction of a cam follower roller may be tolerated at lowcyclic speeds. When the follower is cycled back and forth at high speeds, velocities of the roller and cam become high, and braking of the roller against the cam face becomes a serious problem upon each reversal of direction.
  • the high-speed article feed or transfer apparatus described herein is intended to overcome problems associated with highspeed transfer operations.
  • the present apparatus is capable of operation at 350 cycles per minute and beyond. Each interrelated movement is produced by positively interlocked ele ments which permit relative motion only in the intended directions.
  • Timing belts are employed to drive the transfer apparatus directly from a rotating shaft which drives the press.
  • a timing belt drives a gear pulley which is attached to a cam drive shaft.
  • Two cylindrical cams are keyed on the drive shaft with the cams thereon in phased displaced relationship.
  • the cams are constructed with radially extended cam flanges which are curved to create the camming or reciprocal motion.
  • Cam follower rollers are positioned on both sides of the cam flange so that the rollers continually rotate in a uniform direction. There is no braking, stopping and reversing direction of the cam follower rollers. The source of wear and backlash is thus eliminated.
  • the cam flange is preferably constructed with a tapering cross section so that its widest dimension is at its base and its smallest dimension is at its axially outward extremity.
  • Follower rollers are tapered so that their smallest dimension is nearest the cam drive shaft. Where the cam flanges linear speed is least, it contacts the smallest circle of the follower roller. Where the cam flanges linear speed is greatest, it contacts the largest circle on the follower. Angular speeds of the follower are constant notwithstanding that the linear speed of the cam and follower increase incrementally with the increased distance from the center of the cam and drive shaft. Thus, there is no frictional cam drive shaft follower interface, and no backlash is developed.
  • Slides which support the cam follower axle ride on surfaces which are lubricated by zigzag lubricating channels. Upper surfaces of the slides are sloped to match the sloping retainer surfaces, which hold the slides inward toward the drive shaft.
  • the cam and slide farther from the drive pulley control the forward and rearward motions of the grooved cam bars which move the carriers in and out.
  • the cam and slide nearer the drive pulley reciprocate the carrier support and carrier bars in which workpiece engaging fingers or grooves are formed. Since the latter apparatus is the heavier of the reciprocating parts, and since it has the longest cyclic movements, acceleration forces are greater than in other parts of the transfer. Consequently, the carrier support and slide connections for the drive rod are aligned as closely as is convenient. Angular movements of the drive rods interconnecting the carrier support and slide are kept to a minimum.
  • the cam and slide which are further away from the drive pulley are similar to the before-described cam and slide.
  • Connecting rods extend forward from the latter slide and connect to the lower flanges of two cranks with parallel vertical axles. Outer ends of the upper flanges of the cranks are connected to cam bars.
  • the cam bars drive the parallel carrier bars in and out between article engaging and disengaging positions before the carrier bars are advanced or are withdrawn.
  • the cam bars are mounted between upper and lower carn slides.
  • the cam bars have apertures which are angularly oriented with respect to longitudinal directions of the bars.
  • Sleeve bearing mounted wheels are placed within the apertures for rotating on axles mounted between the slide plates. As the cam bars are reciprocated longitudinally, the slope of the apertures causes the cam bars to be translated at angles to the longitudinal directions.
  • the carrier bars are attached to the cam bars to permit free relative sliding movement therebetween in longitudinal directions of the bars.
  • the interconnections between the bars prevent relative transverse movement. Consequently, the carrier bars undergo the transverse component of the angular movement of the cam bars, while the cam bars slide longitudinally with respect to the carrier bars.
  • the carrier bars move longitudinally with the cam and slide which are closest the drive pulley and move in and out according to movements of the other cam and slide which are communicated through the cam bars.
  • camming means between the fixed frame or slide and the movable camming bar.
  • cam follower axles might be mounted in the cam bars and angular apertures might be cut in the cam slides.
  • the present invention provides a reciprocating support on which the cam bars are mounted.
  • parallel shafts are mounted on the transfer or press frame.
  • the shafts are mounted at their ends to the frame of the transfer or press.
  • Antifriction ball bearing slides surround portions of the shafts move back and forth thereon.
  • Carrier supports are mounted on the antifriction slides, which, with the shafts, insure pure forward and rearward reciprocation of the supports.
  • Upper surfaces of the supports are bearing surfaces for the carrier bars. The upper surfaces of the supports are configured for cooperating with the carrier bars to prevent forward and rearward movement between the carrier bars and the supports but to permit free lateral or transverse movement of the carrier bars.
  • One object of the invention is the provision of a high-speed horizontal transfer apparatus with positively controlled interrelated movements between elements.
  • Another object of this invention is the provision of horizontally movable transfer carriers and interconnected cam bars.
  • Another object of the invention is the provision of flanged cams with double tapered roller slide interconnections.
  • FIG. 5 is a side elevational detail of the carrier bar support.
  • FIG. 6 is a cross-sectional elevation detail of the carrier bar, carrier support and cam bar.
  • a timing belt 12 turns a gear 110 in a direct relation to cyclic operations of a press.
  • timing belt 12 is connected to a press drive shaft which, for example, may extend outward from an upper portion of a press.
  • Pulley 110 is keyed to transfer drive shaft 108.
  • a first cylindrical cam body 120 which has a cam flange 128 radially extending therefrom.
  • Cam flange 128 forms a smooth curve with portions of the cam positionally varying with respect to an axial direction of drive shaft 108.
  • thickness at root 126 is greater than thickness at radial outward extremity 128.
  • Cam 120 reciprocates slide 134 by the action of two wheels 130 which are mounted on either side of the cam flange 128 and which are connected with axles to slide I34.
  • a second cylindrical body 160 supports a radially extending cam flange 164 which drives follower roller 166.
  • the cam follower rollers are mounted on axles 168 which are mounted in slide 170 and which extend downward therefrom on opposite sides of cam flange 164.
  • Rods 40 have first ends connected to pins which extend outward from opposite sides of slide 170. Forward ends of rods 40 are connected through clevises 44 to carriers 50 which are schematically represented for clarity as single elements.
  • Carrier bars 50 have recesses 52 and fingers 54 which grip articles to be transferred step by step between die stations in a press.
  • Rods 40, slide 170 and cam 160 reciprocate the carriers forward and rearward. Inward and outward motion is imparted to carrier bars 50 by cam bars 60. The latter are driven back and forth through linkage which is moved by slide 134 and cam 120.
  • Rods 62 are connected to a forward edge of slide 154. Forward ends of the rods are connected to lower flanges 64 of cranks 66. Upper flanges 68 of the cranks are connected through rod 69 to the cam bars 60.
  • Each cam bar has several cam apertures 70 which are disposed in the cam bar at an angle to a longitudinal direction of the cam bar.
  • Upper and lower cam slides 72 and 74 hold axles on which cam follower wheels 76 are mounted.
  • wheels 76 bear upon the cam apertures 70 causing the bars to translate angularly in a horizontal plane.
  • Elongated hooked shaped interconnections 80 and 82 between the cam bar and carrier permit relative longitudinal sliding but prevent relative transverse motion of the bars. Therefore, carrier bar 50 undergoes the transverse component of the translation of cam bars 60.
  • FIG. 2 the carrier bar 50 and cam bar 60 are shown interconnected and partially exposed.
  • Rod 40 is connected through a ball joint 90 to a pin 92 which is mounted in a support which reciprocates the carrier bar 50 longitudinally.
  • Rods 69 are connected between upper flanges 68 of cranks 66 and clevises 94, which are mounted on ends of cam bars 60. Cranks 66 rotate on vertical axles 95.
  • Upper cam slides 72 hold vertical axles 96 upon which skate wheels 76 are mounted. Skate wheels 76 are disposed within cam apertures 70 in cam bars 60. As shown in the drawing, the cam bars are in rearward or leftmost position. When the cam bars are moved forward, the angularly oriented walls of apertures 70 cause the cam bars to move inward. Since there are several apertures and skate wheels, the entire bars translate angularly in a forward and inward direction in a horizontal plane. As that happens, carrier bars 50 are pushed inward, so that the recesses 52 and teeth 54 engage articles 96 in the die stations 98.
  • Rods 40 are then driven forward, pushing carrier bars 50 and articles engaged thereby forward to the next die stations.
  • that transfer action occurs as the upper die is being lifted by the press.
  • a cam base which is part of the fixed transfer frame is configured similar to well-known crankcases.
  • the upper surface of the base or frame is a sliding surface with oil groove lubrication.
  • Base 100 is sealed at both ends 102 and 104, where tapered roller bearings support the shaft for rotation.
  • One end of drive shaft 108 mounts a gear-toothed pulley which is keyed to the drive shafi.
  • a timing belt drives the pulley 110.
  • the cylindrical body 122 of a first drive cam is keyed to drive shaft 108 at a remote location thereon from the drive pulley.
  • a cam flange 124 extends radially from body 122 and smoothly incrementally varies axial position around the circumference of the body.
  • Cam flange 124 is tapered from a maximum cross-sectional dimension adjacent root I26 to a minimum cross-sectional dimension adjacent outer edge I28.
  • Cam follower rollers are mounted on opposite sides of the cam flange.
  • Rollers 130 are tapered complimentary to the cam flange taper.
  • Parallel axles 132 extend upward from the cam followers and are mounted in a first slide 134.
  • upper surfaces 136 of the slide body are sloped, whereas lower surfaces 138 are flat. Lower surfaces 138 ride on sliding surfaces 140 which are lubricated by passageways 142. The sloping upper surfaces are engaged by complimentary sloping surfaces 144 of retainers I46 which are lubricated by oil passages I48. Rod 62 which drives the crank and cam bar is connected to a plate secured at the forward end of slide 134.
  • a second cam is connected to the drive shaft near the drive pulley.
  • the second cam, cam followers and slide are configured closely similar to the first cam, and the identification numbers are similar to identify the elements.
  • One difference between cam 120 and cam 160 is that the latter has a greater cyclic travel.
  • Cam flange 164 drive cam follower rollers 166.
  • the rollers are mounted on shaft 168 in slide 170.
  • Oil channels 142 and 148 serve sliding surfaces 140 and 144 as shown in FIG. 4.
  • Slide 170 is connected to rod 40 which drives the carrier apparatus.
  • rod 40 is connected to a clevis which is mounted on slide support 182.
  • the slid support rests upon an antifriction bearing 184 which surrounds a portion of shaft 186.
  • Shaft 186 is mounted at ends thereof with mounts 188 which are anchored on the transfer or press frame 190.
  • the slide support 182 is shown in a cross-sectional detail of FIG. 6. Shafis 186 support bearing 184 which surrounds portions of the shaft. The slide support 182 is fixed to the hearing so that support 182 moves forward and rearward or in and out of the drawing plane in pure reciprocation. Carrier bar 50 slides on an upper surface I90 of support 182. A key 192 and a keyway 194 permit lateral movement of carrier bar 50 and support 182 but prevent relative longitudinal movement.
  • the downward hooked portion 80 of cam bar 60 fits within a groove 196 in carrier bar attachment portion 198.
  • Article transfer apparatus comprising:
  • first and second cam means comprising cam apertures angularly disposed with respect to an elongated direction of the cam bar
  • the second cam means comprising cam followers positioned in the apertures and having axles extending outward therefrom, one of the cam means being fixed in the cam bar, and the other of the cam means being fixed in the frame
  • an elongated carrier mounted on the frame parallel to the cam bar and connected to the cam bar for free relative sliding movement relative to the frame and for free longitudinal sliding movement relative to the cam bar and for lateral movement with the cam bar, the elongated carrier having article engaging means on one side thereof,
  • first reciprocating means connected to the cam bar for moving the cam bar forward and rearward in a longitudinal direction thereof, thereby causing angular translational movement of the cam bar by interaction of the first and second cam means
  • timing means connected to the first and second reciprocating means for operating the reciprocating means in phasedisplaced relation, whereby the cam bar and carrier move longitudinally at different times.
  • first cam means apertures are disposed in the cam bar and wherein the second cam means followers comprise wheels disposed within the apertures and axles extending outward therefrom and fixed in the cam slide.
  • the carrier mounting comprises elongated shafts mounted on the frame parallel to the carrier and beneath the carrier, and antifriction bearings surrounding portions of the shafts, a carrier support fixed to upper portions of the bearings, the carrier support having an upper sliding surface, elongated carrier bars mounted on the sliding surface, groove and lug interconnection means on the sliding surface and the carrier bar and the interconnection means being oriented transverse to an elongated direction thereof for permitting lateral movement of a carrier bar with respect to the support and for preventing relative longitudinal motion therebetween, and wherein a cam bar engaging means is formed on a side of the carrier bar opposite the article engaging means, and wherein the second reciprocating means is connected to the carrier support for moving the support forward and rearward on the shafts and for driving the carrier bar forward and rearward with the carrier su rt.
  • the timing means comprises a drive shaft mounted for rotation on the frame, and means for rotating the drive shaft
  • the first reciprocating means comprises a first cylindrical body keyed to the drive shaft and having a cam flange extending radially therefrom at a smoothly varying axial position with respect to the drive shaft, cam follower rollers mounted on opposite sides of the cam flange, and axles extending upward from the follower rollers, a slide connected to the axles and having a lower surface configured for sliding on the frame and a linkage interconnecting the slide and the cam bar
  • the second reciprocating means comprises a second cylindrical body keyed to the drive shaft and a second radially extending cam flange having smoothly varying axial position mounted on the second body, second cam follower rollers mounted on opposite sides of the second cam flange, axles extending upward from the follower rollers, and a second slide rigidly supporting the axles, the second slide having a lower surface configured for sliding along the frame in a
  • first linkage comprises a first connecting rod extending from the first slide toward the cam bar, a crank having a vertical axis and having a lower radial flange connected at an outer end thereof to a second end of the first rod, the crank having a second flange extending radially outward with an outer end connected to a first end of a second rod having a second end connected to the cam bar.
  • the transfer apparatus of claim 1 further comprising a second cam slide mounted on the frame parallel to the first cam slide, a second cam bar mounted on the second cam slide parallel to the first cam bar, third and fourth cam means interconnecting the frame and the second cam bar, a second carrier slidably mounted on the frame parallel to the second cam bar and connected thereto for lateral movement therewith, wherein the first and second carriers define an article receiving and treating space therebetween.

Abstract

High-speed transfer apparatus for presses has spaced carrier bars with inward article receiving configurations. The carrier bars are mounted on carrier supports for longitudinal movement therewith and for relative transverse movement with respect thereto. The carrier bars are positively connected to the cam bars for lateral in and out movement therewith and for relative sliding. The carrier supports and cam bars are independently reciprocated in phase displaced relationship so the carrier bar moves forward after the cam bar has moved inward, and so the cam bar draws the carrier outward before the carrier is returned to its first position. The carrier and cam bar are reciprocated by separate rotating cams and followers. A cam flange extends radially outward from a cylindrical body and followers are mounted on opposite sides of the flange for continuous uniform direction rotation of the followers as the cam rotates, and the followers move slides which are connected to the cam bar and carrier bar.

Description

United States Patent [72] inventor Stuart H. McCaughey P.O. Box 255, Cockeysville Road, Cockeysville, Md. 21030 211 Appl. No. 25,725 [22] Filed Apr. 6, 1970 [45] Patented Nov. 16, 1971 Continuation-in-part of application Ser. No. 713,830, Mar. 18, 1968. This application Apr. 6, 1970, Ser. No. 25,725
[54] HORIZONTAL HIGH-SPEED TRANSFER 7 Claims, 6 Drawing Figs.
[52] U.S.Cl.. 214/1 [51 Int. Cl 865g 25/04 [50] Field of Search 2l4/ l B [5 6] References Cited UNITED STATES PATENTS 3,430,782 3/l969 Henkel 214/1 B FOREIGN PATENTS 597,324 5/1960 Canada 214/] B Primary ExaminerGerald M. Forlenza Assistant Examiner-George F. Abraham At!0rney--Littlepage, Quaintance, Wray & Aisenberg ABSTRACT: High-speed transfer apparatus for presses has spaced carrier bars with inward article receiving configurations. The carrier bars are mounted on carrier supports for longitudinal movement therewith and for relative transverse movement with respect thereto. The carrier bars are positively connected to the cam bars for lateral in and out movement therewith and for relative sliding. The carrier supports and cam bars are independently reciprocated in phase displaced relationship so the carrier bar moves forward after the cam bar has moved inward, and so the cam bar draws the carrier outward before the carrier is returned to its first position. The carrier and cam bar are reciprocated by separate rotating cams and followers. A cam flange extends radially outward from a cylindrical body and followers are mounted on opposite sides of the flange for continuous uniform direction rotation of the followers as the cam rotates, and the followers move slides which are connected to the cam bar and carrier bar.
PAIENTEUunv 1s |97l SHEET 2 BF 6 INVENTOR PATENTEnunv 16 Ian 3.620.381
SHEET 3 BF 6 INVI'INTORS STUART H. McCAUGHEY PATENTEnunv 16 Ian SHEET 6 OF 6 INVENTOR STUART H. MOCAUGHEY m @Fm HORIZONTAL HIGH-SPEED TRANSFER BACKGROUND OF THE INVENTION This application is a continuation-in-part of U.S. Pat. application Ser. No. 713,830, filed on Mar. 18, I968, row Pat. No. 3,528,575 by Stuart H. McCaughey for Feed and Transfer Systems.
Very high-speed press operations are made possible by new tool materials and press designs. One area which has limited the speed of press operations is the transfer apparatus which is used to feed articles from station to station in presses. Article feed or transfer apparatus has heretofore employed springs which required excessive operational times to move a part from one position to another. During the rapid accelerations while being transfered between work stations, workpieces which are not well engaged and held tend to float and misalign, jamming the machinery, or causing high-rejection rates, and necessitating high percentages of inspection and sampling. Forces which cause floating and misalignment increase geometrically with increasing cyclic speeds.
Movements must be very accurate in all transfers. In highspeed transfers, the accuracy of the transfer movements becomes critical. Play or backlash in transfer apparatus causes many problems which cannot be tolerated in high-speed equipment. Because of the increased accelerations, many conditions which are completely workable at low speeds, become destructive at high speeds. For example, the periodic reversing of direction of a cam follower roller may be tolerated at lowcyclic speeds. When the follower is cycled back and forth at high speeds, velocities of the roller and cam become high, and braking of the roller against the cam face becomes a serious problem upon each reversal of direction.
SUMMARY OF THE INVENTION The high-speed article feed or transfer apparatus described herein is intended to overcome problems associated with highspeed transfer operations. The present apparatus is capable of operation at 350 cycles per minute and beyond. Each interrelated movement is produced by positively interlocked ele ments which permit relative motion only in the intended directions.
Timing belts are employed to drive the transfer apparatus directly from a rotating shaft which drives the press. A timing belt drives a gear pulley which is attached to a cam drive shaft. Two cylindrical cams are keyed on the drive shaft with the cams thereon in phased displaced relationship. In a preferred form, the cams are constructed with radially extended cam flanges which are curved to create the camming or reciprocal motion. Cam follower rollers are positioned on both sides of the cam flange so that the rollers continually rotate in a uniform direction. There is no braking, stopping and reversing direction of the cam follower rollers. The source of wear and backlash is thus eliminated.
The cam flange is preferably constructed with a tapering cross section so that its widest dimension is at its base and its smallest dimension is at its axially outward extremity. Follower rollers are tapered so that their smallest dimension is nearest the cam drive shaft. Where the cam flanges linear speed is least, it contacts the smallest circle of the follower roller. Where the cam flanges linear speed is greatest, it contacts the largest circle on the follower. Angular speeds of the follower are constant notwithstanding that the linear speed of the cam and follower increase incrementally with the increased distance from the center of the cam and drive shaft. Thus, there is no frictional cam drive shaft follower interface, and no backlash is developed.
Slides which support the cam follower axle ride on surfaces which are lubricated by zigzag lubricating channels. Upper surfaces of the slides are sloped to match the sloping retainer surfaces, which hold the slides inward toward the drive shaft.
The cam and slide farther from the drive pulley control the forward and rearward motions of the grooved cam bars which move the carriers in and out. The cam and slide nearer the drive pulley reciprocate the carrier support and carrier bars in which workpiece engaging fingers or grooves are formed. Since the latter apparatus is the heavier of the reciprocating parts, and since it has the longest cyclic movements, acceleration forces are greater than in other parts of the transfer. Consequently, the carrier support and slide connections for the drive rod are aligned as closely as is convenient. Angular movements of the drive rods interconnecting the carrier support and slide are kept to a minimum.
The cam and slide which are further away from the drive pulley are similar to the before-described cam and slide. Connecting rods extend forward from the latter slide and connect to the lower flanges of two cranks with parallel vertical axles. Outer ends of the upper flanges of the cranks are connected to cam bars. The cam bars drive the parallel carrier bars in and out between article engaging and disengaging positions before the carrier bars are advanced or are withdrawn. The cam bars are mounted between upper and lower carn slides. In a preferred form of the invention the cam bars have apertures which are angularly oriented with respect to longitudinal directions of the bars. Sleeve bearing mounted wheels are placed within the apertures for rotating on axles mounted between the slide plates. As the cam bars are reciprocated longitudinally, the slope of the apertures causes the cam bars to be translated at angles to the longitudinal directions.
The carrier bars are attached to the cam bars to permit free relative sliding movement therebetween in longitudinal directions of the bars. The interconnections between the bars prevent relative transverse movement. Consequently, the carrier bars undergo the transverse component of the angular movement of the cam bars, while the cam bars slide longitudinally with respect to the carrier bars. The carrier bars move longitudinally with the cam and slide which are closest the drive pulley and move in and out according to movements of the other cam and slide which are communicated through the cam bars.
The objects of the invention may be carried out with several forms of camming means between the fixed frame or slide and the movable camming bar. For example, cam follower axles might be mounted in the cam bars and angular apertures might be cut in the cam slides.
For accurate longitudinal step by step advancement of the articles and for maintaining the desired connection between the carrier bars and the cam bars, the present invention provides a reciprocating support on which the cam bars are mounted. In a preferred form of the invention, parallel shafts are mounted on the transfer or press frame. The shafts are mounted at their ends to the frame of the transfer or press. Antifriction ball bearing slides surround portions of the shafts move back and forth thereon. Carrier supports are mounted on the antifriction slides, which, with the shafts, insure pure forward and rearward reciprocation of the supports. Upper surfaces of the supports are bearing surfaces for the carrier bars. The upper surfaces of the supports are configured for cooperating with the carrier bars to prevent forward and rearward movement between the carrier bars and the supports but to permit free lateral or transverse movement of the carrier bars.
One object of the invention is the provision of a high-speed horizontal transfer apparatus with positively controlled interrelated movements between elements.
Another object of this invention is the provision of horizontally movable transfer carriers and interconnected cam bars.
Another object of the invention is the provision of flanged cams with double tapered roller slide interconnections.
These and other objects of the invention will be apparent from the disclosure which is found in the foregoing and detailed specification portions as well as in the claims and in the drawings.
BRIEF DESCRIPTION OF THE DRAWINGS cam and follower.
FIG. 5 is a side elevational detail of the carrier bar support.
FIG. 6 is a cross-sectional elevation detail of the carrier bar, carrier support and cam bar.
DETAILED DESCRIPTION OF THE DRAWINGS Transfer apparatus is generally indicated by numeral 10 in FIG. 1. A timing belt 12 turns a gear 110 in a direct relation to cyclic operations of a press. Preferably, timing belt 12 is connected to a press drive shaft which, for example, may extend outward from an upper portion of a press. Pulley 110 is keyed to transfer drive shaft 108. Also keyed to the drive shaft is a first cylindrical cam body 120 which has a cam flange 128 radially extending therefrom. Cam flange 128 forms a smooth curve with portions of the cam positionally varying with respect to an axial direction of drive shaft 108. In a preferred form of the cam, thickness at root 126 is greater than thickness at radial outward extremity 128. Cam 120 reciprocates slide 134 by the action of two wheels 130 which are mounted on either side of the cam flange 128 and which are connected with axles to slide I34. A second cylindrical body 160 supports a radially extending cam flange 164 which drives follower roller 166. The cam follower rollers are mounted on axles 168 which are mounted in slide 170 and which extend downward therefrom on opposite sides of cam flange 164. Rods 40 have first ends connected to pins which extend outward from opposite sides of slide 170. Forward ends of rods 40 are connected through clevises 44 to carriers 50 which are schematically represented for clarity as single elements. Carrier bars 50 have recesses 52 and fingers 54 which grip articles to be transferred step by step between die stations in a press. Rods 40, slide 170 and cam 160 reciprocate the carriers forward and rearward. Inward and outward motion is imparted to carrier bars 50 by cam bars 60. The latter are driven back and forth through linkage which is moved by slide 134 and cam 120. Rods 62 are connected to a forward edge of slide 154. Forward ends of the rods are connected to lower flanges 64 of cranks 66. Upper flanges 68 of the cranks are connected through rod 69 to the cam bars 60.
Each cam bar has several cam apertures 70 which are disposed in the cam bar at an angle to a longitudinal direction of the cam bar. Upper and lower cam slides 72 and 74 hold axles on which cam follower wheels 76 are mounted. As the cam bars 60 are driven forward and rearward by the linkage, wheels 76 bear upon the cam apertures 70 causing the bars to translate angularly in a horizontal plane. As cam bars 60 translate, the transverse component of the translation is imparted to carriers 50. Elongated hooked shaped interconnections 80 and 82 between the cam bar and carrier permit relative longitudinal sliding but prevent relative transverse motion of the bars. Therefore, carrier bar 50 undergoes the transverse component of the translation of cam bars 60.
In FIG. 2 the carrier bar 50 and cam bar 60 are shown interconnected and partially exposed. Rod 40 is connected through a ball joint 90 to a pin 92 which is mounted in a support which reciprocates the carrier bar 50 longitudinally.
Rods 69 are connected between upper flanges 68 of cranks 66 and clevises 94, which are mounted on ends of cam bars 60. Cranks 66 rotate on vertical axles 95.
Upper cam slides 72 hold vertical axles 96 upon which skate wheels 76 are mounted. Skate wheels 76 are disposed within cam apertures 70 in cam bars 60. As shown in the drawing, the cam bars are in rearward or leftmost position. When the cam bars are moved forward, the angularly oriented walls of apertures 70 cause the cam bars to move inward. Since there are several apertures and skate wheels, the entire bars translate angularly in a forward and inward direction in a horizontal plane. As that happens, carrier bars 50 are pushed inward, so that the recesses 52 and teeth 54 engage articles 96 in the die stations 98.
Rods 40 are then driven forward, pushing carrier bars 50 and articles engaged thereby forward to the next die stations. Preferably, that transfer action occurs as the upper die is being lifted by the press.
On the down stroke of the press, slid 26 moves forward, turning cranks 66, and drawing rods 69 and cam bars 60 rearward. The action of skate wheels 76 and cam apertures 70 causes the cam bars to translate outwardly and rearwardly, drawing the carrier bars 50 outward, and disengaging the carrier from the articles which remain in the die stations. As soon as the carrier bars have been disengagedfrom the articles, rods 40 may be rearward, returning the carrier bars 50 to their original rearward positions.
Referring to FIG. 3, a cam base which is part of the fixed transfer frame is configured similar to well-known crankcases. The upper surface of the base or frame is a sliding surface with oil groove lubrication. Base 100 is sealed at both ends 102 and 104, where tapered roller bearings support the shaft for rotation.
One end of drive shaft 108 mounts a gear-toothed pulley which is keyed to the drive shafi. A timing belt drives the pulley 110.
The cylindrical body 122 of a first drive cam is keyed to drive shaft 108 at a remote location thereon from the drive pulley. A cam flange 124 extends radially from body 122 and smoothly incrementally varies axial position around the circumference of the body. Cam flange 124 is tapered from a maximum cross-sectional dimension adjacent root I26 to a minimum cross-sectional dimension adjacent outer edge I28. Cam follower rollers are mounted on opposite sides of the cam flange. Rollers 130 are tapered complimentary to the cam flange taper. Parallel axles 132 extend upward from the cam followers and are mounted in a first slide 134.
As shown in FIG. 4, upper surfaces 136 of the slide body are sloped, whereas lower surfaces 138 are flat. Lower surfaces 138 ride on sliding surfaces 140 which are lubricated by passageways 142. The sloping upper surfaces are engaged by complimentary sloping surfaces 144 of retainers I46 which are lubricated by oil passages I48. Rod 62 which drives the crank and cam bar is connected to a plate secured at the forward end of slide 134.
A second cam is connected to the drive shaft near the drive pulley. The second cam, cam followers and slide are configured closely similar to the first cam, and the identification numbers are similar to identify the elements. One difference between cam 120 and cam 160 is that the latter has a greater cyclic travel. Cam flange 164 drive cam follower rollers 166. The rollers are mounted on shaft 168 in slide 170. Oil channels 142 and 148 serve sliding surfaces 140 and 144 as shown in FIG. 4. Slide 170 is connected to rod 40 which drives the carrier apparatus.
As shown in the detail of FIG. 5, rod 40 is connected to a clevis which is mounted on slide support 182. The slid support rests upon an antifriction bearing 184 which surrounds a portion of shaft 186. Shaft 186 is mounted at ends thereof with mounts 188 which are anchored on the transfer or press frame 190.
The slide support 182 is shown in a cross-sectional detail of FIG. 6. Shafis 186 support bearing 184 which surrounds portions of the shaft. The slide support 182 is fixed to the hearing so that support 182 moves forward and rearward or in and out of the drawing plane in pure reciprocation. Carrier bar 50 slides on an upper surface I90 of support 182. A key 192 and a keyway 194 permit lateral movement of carrier bar 50 and support 182 but prevent relative longitudinal movement.
The downward hooked portion 80 of cam bar 60 fits within a groove 196 in carrier bar attachment portion 198. The
hooklike portion 82 of the carrier bar section 198 fits in a similar groove 199 in the cam bar. Thus, the carrier bar 50 and cam bar 60 are permitted to slide longitudinally relative to each other, but the carrier bar and cam bar are firmly interconnected to move laterally together.
Although the invention has been described with reference to specific embodiments, it will be appreciated by those skilled in the art that other embodiments may be constructed without departing from the teachings of the invention. The scope of the invention is defined only in the following claims.
That which is claimed is:
1. Article transfer apparatus comprising:
a frame,
a cam slide having a horizontal sliding surface fixed to the frame,
an elongated cam bar mounted on the horizontal sliding surface of the slide for movement thereon,
first and second cam means, the first cam means comprising cam apertures angularly disposed with respect to an elongated direction of the cam bar, and the second cam means comprising cam followers positioned in the apertures and having axles extending outward therefrom, one of the cam means being fixed in the cam bar, and the other of the cam means being fixed in the frame,
an elongated carrier mounted on the frame parallel to the cam bar and connected to the cam bar for free relative sliding movement relative to the frame and for free longitudinal sliding movement relative to the cam bar and for lateral movement with the cam bar, the elongated carrier having article engaging means on one side thereof,
first reciprocating means connected to the cam bar for moving the cam bar forward and rearward in a longitudinal direction thereof, thereby causing angular translational movement of the cam bar by interaction of the first and second cam means,
second reciprocating means connected to the carrier for moving the carrier forward and rearward in a longitudinal direction thereof,
timing means connected to the first and second reciprocating means for operating the reciprocating means in phasedisplaced relation, whereby the cam bar and carrier move longitudinally at different times.
2. The transfer apparatus of claim 1 wherein the first cam means apertures are disposed in the cam bar and wherein the second cam means followers comprise wheels disposed within the apertures and axles extending outward therefrom and fixed in the cam slide.
3. The transfer apparatus of claim 1 wherein the carrier has at a second side thereof opposite the article engaging surface an outward and upward extending elongated portion having a hooklike cross section, and wherein the cam bar has at a lateral side thereof adjacent the carrier an elongated portion having a complementary hooklike cross section which is interconnected with the portion of the carrier, permitting relative longitudinal sliding between the carrier and cam bar, and preventing relative lateral movement therebetween.
4. The transfer apparatus of claim 1 wherein the carrier mounting comprises elongated shafts mounted on the frame parallel to the carrier and beneath the carrier, and antifriction bearings surrounding portions of the shafts, a carrier support fixed to upper portions of the bearings, the carrier support having an upper sliding surface, elongated carrier bars mounted on the sliding surface, groove and lug interconnection means on the sliding surface and the carrier bar and the interconnection means being oriented transverse to an elongated direction thereof for permitting lateral movement of a carrier bar with respect to the support and for preventing relative longitudinal motion therebetween, and wherein a cam bar engaging means is formed on a side of the carrier bar opposite the article engaging means, and wherein the second reciprocating means is connected to the carrier support for moving the support forward and rearward on the shafts and for driving the carrier bar forward and rearward with the carrier su rt. I
5. he transfer apparatus of claim 1 wherein the timing means comprises a drive shaft mounted for rotation on the frame, and means for rotating the drive shaft, and wherein the first reciprocating means comprises a first cylindrical body keyed to the drive shaft and having a cam flange extending radially therefrom at a smoothly varying axial position with respect to the drive shaft, cam follower rollers mounted on opposite sides of the cam flange, and axles extending upward from the follower rollers, a slide connected to the axles and having a lower surface configured for sliding on the frame and a linkage interconnecting the slide and the cam bar, and wherein the second reciprocating means comprises a second cylindrical body keyed to the drive shaft and a second radially extending cam flange having smoothly varying axial position mounted on the second body, second cam follower rollers mounted on opposite sides of the second cam flange, axles extending upward from the follower rollers, and a second slide rigidly supporting the axles, the second slide having a lower surface configured for sliding along the frame in a movement controlled by the second cam flange and second follower rollers, and second linkage means interconnecting the second slide carrier.
6. The transfer apparatus of claim 5 wherein the first linkage comprises a first connecting rod extending from the first slide toward the cam bar, a crank having a vertical axis and having a lower radial flange connected at an outer end thereof to a second end of the first rod, the crank having a second flange extending radially outward with an outer end connected to a first end of a second rod having a second end connected to the cam bar.
7. The transfer apparatus of claim 1 further comprising a second cam slide mounted on the frame parallel to the first cam slide, a second cam bar mounted on the second cam slide parallel to the first cam bar, third and fourth cam means interconnecting the frame and the second cam bar, a second carrier slidably mounted on the frame parallel to the second cam bar and connected thereto for lateral movement therewith, wherein the first and second carriers define an article receiving and treating space therebetween.

Claims (7)

1. Article transfer apparatus comprising: a frame, a cam slide having a horizontal sliding surface fixed to the frame, an elongated cam bar mounted on the horizontal sliding surface of the slide for movement thereon, first and second cam means, the first cam means comprising cam apertures angularly disposed with respect to an elongated direction of the cam bar, and the second cam means comprising cam followers positioned in the apertures and having axles extending outward therefrom, one of the cam means being fixed in the cam bar, and the other of the cam means being fixed in the frame, an elongated carrier mounted on the frame parallel to the cam bar and connected to the cam bar for free relative sliding movement relative to the frame and for free longitudinal sliding movement relative to the cam bar and for lateral movement with the cam bar, the elongated carrier having article engaging means on one side thereof, first reciprocating means connected to the cam bar for moving the cam bar forward and rearward in a longitudinal direction thereof, thereby causing angular translational movement of the cam bar by interaction of the first and second cam means, second reciprocating means connected to the carrier for moving the carrier forward and rearward in a longitudinal direction thereof, timing means connected to the first and second reciprocating means for operating the reciprocating means in phase-displaced relation, whereby the cam bar and carrier move longitudinally at different times.
2. The tRansfer apparatus of claim 1 wherein the first cam means apertures are disposed in the cam bar and wherein the second cam means followers comprise wheels disposed within the apertures and axles extending outward therefrom and fixed in the cam slide.
3. The transfer apparatus of claim 1 wherein the carrier has at a second side thereof opposite the article engaging surface an outward and upward extending elongated portion having a hooklike cross section, and wherein the cam bar has at a lateral side thereof adjacent the carrier an elongated portion having a complementary hooklike cross section which is interconnected with the portion of the carrier, permitting relative longitudinal sliding between the carrier and cam bar, and preventing relative lateral movement therebetween.
4. The transfer apparatus of claim 1 wherein the carrier mounting comprises elongated shafts mounted on the frame parallel to the carrier and beneath the carrier, and antifriction bearings surrounding portions of the shafts, a carrier support fixed to upper portions of the bearings, the carrier support having an upper sliding surface, elongated carrier bars mounted on the sliding surface, groove and lug interconnection means on the sliding surface and the carrier bar and the interconnection means being oriented transverse to an elongated direction thereof for permitting lateral movement of a carrier bar with respect to the support and for preventing relative longitudinal motion therebetween, and wherein a cam bar engaging means is formed on a side of the carrier bar opposite the article engaging means, and wherein the second reciprocating means is connected to the carrier support for moving the support forward and rearward on the shafts and for driving the carrier bar forward and rearward with the carrier support.
5. The transfer apparatus of claim 1 wherein the timing means comprises a drive shaft mounted for rotation on the frame, and means for rotating the drive shaft, and wherein the first reciprocating means comprises a first cylindrical body keyed to the drive shaft and having a cam flange extending radially therefrom at a smoothly varying axial position with respect to the drive shaft, cam follower rollers mounted on opposite sides of the cam flange, and axles extending upward from the follower rollers, a slide connected to the axles and having a lower surface configured for sliding on the frame and a linkage interconnecting the slide and the cam bar, and wherein the second reciprocating means comprises a second cylindrical body keyed to the drive shaft and a second radially extending cam flange having smoothly varying axial position mounted on the second body, second cam follower rollers mounted on opposite sides of the second cam flange, axles extending upward from the follower rollers, and a second slide rigidly supporting the axles, the second slide having a lower surface configured for sliding along the frame in a movement controlled by the second cam flange and second follower rollers, and second linkage means interconnecting the second slide carrier.
6. The transfer apparatus of claim 5 wherein the first linkage comprises a first connecting rod extending from the first slide toward the cam bar, a crank having a vertical axis and having a lower radial flange connected at an outer end thereof to a second end of the first rod, the crank having a second flange extending radially outward with an outer end connected to a first end of a second rod having a second end connected to the cam bar.
7. The transfer apparatus of claim 1 further comprising a second cam slide mounted on the frame parallel to the first cam slide, a second cam bar mounted on the second cam slide parallel to the first cam bar, third and fourth cam means interconnecting the frame and the second cam bar, a second carrier slidably mounted on the frame parallel to the second cam bar and connected thereto for lateral movement therewith, wherein the first and second carriers define an article receiving and treating spaCe therebetween.
US25725A 1970-04-06 1970-04-06 Horizontal high-speed transfer Expired - Lifetime US3620381A (en)

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4006829A (en) * 1975-04-15 1977-02-08 Citizen Watch Co., Ltd. Transfer unit in a transfer machine
US4016984A (en) * 1975-08-28 1977-04-12 Eaton Corporation Shuttle assembly for a load handling apparatus
US4032018A (en) * 1975-11-21 1977-06-28 Wallis Bernard J Workpiece transfer mechanism
US4089203A (en) * 1976-04-07 1978-05-16 Wallis Bernard J Workpiece transfer mechanism
DE2756096A1 (en) * 1976-12-23 1978-06-29 Gulf & Western Mfg Co TRANSPORT DEVICE, IN PARTICULAR FOR THE STEP-BY-STEP TRANSPORT OF WORK PIECES IN PRESSES
FR2375000A1 (en) * 1976-12-23 1978-07-21 Gulf & Western Mfg Co PARTS TRANSFER MECHANISM
DE2839934A1 (en) * 1977-09-19 1979-03-29 Gulf & Western Mfg Co FEED DEVICE
US4256218A (en) * 1978-06-27 1981-03-17 M. S. Willett, Inc. Three axis transfer apparatus
US4359153A (en) * 1978-06-27 1982-11-16 M. S. Willett, Inc. Three axis transfer apparatus
US4462738A (en) * 1979-01-22 1984-07-31 M. S. Willett, Inc. Feed and transfer system
US4532820A (en) * 1978-06-27 1985-08-06 M. S. Willett, Inc. Motion multiplier apparatus
US4960197A (en) * 1988-03-16 1990-10-02 Asahi-Sieki Manufacturing Co., Ltd. Finger actuating device in a transfer press
US5136874A (en) * 1989-11-06 1992-08-11 Rapindex Incorporated Indexing conveyor for a die transfer system
US5346055A (en) * 1992-07-16 1994-09-13 Zierpka Guenter Machinery for discontinuously forwarding material or work past or through discontinuously operating tools
US5975284A (en) * 1996-11-11 1999-11-02 Sankyo Manufacturing Co., Ltd. Carrier apparatus
WO2023084187A1 (en) * 2021-11-11 2023-05-19 Ishida Europe Limited Container transfer apparatus, system and methods

Citations (2)

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CA597324A (en) * 1960-05-03 W. Jacobs Orville Transfer apparatus
US3430782A (en) * 1967-06-29 1969-03-04 Edward J Henkel Article transfer apparatus

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Publication number Priority date Publication date Assignee Title
CA597324A (en) * 1960-05-03 W. Jacobs Orville Transfer apparatus
US3430782A (en) * 1967-06-29 1969-03-04 Edward J Henkel Article transfer apparatus

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4006829A (en) * 1975-04-15 1977-02-08 Citizen Watch Co., Ltd. Transfer unit in a transfer machine
US4016984A (en) * 1975-08-28 1977-04-12 Eaton Corporation Shuttle assembly for a load handling apparatus
US4032018A (en) * 1975-11-21 1977-06-28 Wallis Bernard J Workpiece transfer mechanism
US4089203A (en) * 1976-04-07 1978-05-16 Wallis Bernard J Workpiece transfer mechanism
DE2756096A1 (en) * 1976-12-23 1978-06-29 Gulf & Western Mfg Co TRANSPORT DEVICE, IN PARTICULAR FOR THE STEP-BY-STEP TRANSPORT OF WORK PIECES IN PRESSES
FR2375000A1 (en) * 1976-12-23 1978-07-21 Gulf & Western Mfg Co PARTS TRANSFER MECHANISM
DE2839934A1 (en) * 1977-09-19 1979-03-29 Gulf & Western Mfg Co FEED DEVICE
US4359153A (en) * 1978-06-27 1982-11-16 M. S. Willett, Inc. Three axis transfer apparatus
US4256218A (en) * 1978-06-27 1981-03-17 M. S. Willett, Inc. Three axis transfer apparatus
US4532820A (en) * 1978-06-27 1985-08-06 M. S. Willett, Inc. Motion multiplier apparatus
US4462738A (en) * 1979-01-22 1984-07-31 M. S. Willett, Inc. Feed and transfer system
US4960197A (en) * 1988-03-16 1990-10-02 Asahi-Sieki Manufacturing Co., Ltd. Finger actuating device in a transfer press
US5107979A (en) * 1988-03-16 1992-04-28 Asahi-Seiki Manufacturing Co., Ltd. Finger actuating device in a transfer press
US5136874A (en) * 1989-11-06 1992-08-11 Rapindex Incorporated Indexing conveyor for a die transfer system
US5346055A (en) * 1992-07-16 1994-09-13 Zierpka Guenter Machinery for discontinuously forwarding material or work past or through discontinuously operating tools
US5975284A (en) * 1996-11-11 1999-11-02 Sankyo Manufacturing Co., Ltd. Carrier apparatus
WO2023084187A1 (en) * 2021-11-11 2023-05-19 Ishida Europe Limited Container transfer apparatus, system and methods

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