Apparatus for protecting light projector from collision with punch of button setting machine

Abstract: A method and apparatus for protecting a horizon­ tally reciprocable light projector (8) from collision with a vertically reciprocable punch (1) of a button setting machine, wherein a lost motion mechanism (21) is provided for producing a delay between retracting movement of the light projector (8) and the downward movement of the punch (1) to such an extent that the light projector (8) is retracted from the vertical path of movement of the punch (1) before the punch (1) starts moving downward. The lost motion mechanism is composed of a shaft (16) having an annular actuating flange (18), and a cylinder member (17) slidably re­ ceiving therein the shaft (16). The actuating flange (18) is normally separated from the cylinder member (17) and engageable with the cylinder member (17) to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1).

Description: The present invention relates generally to a button setting machine having an optical position indicator for indicating an accurate position on the garment fabric where upper and lower elements of a fastener, such as a stud button for denim jeans, are to be attached by and between a punch and a die of the button setting machine. The present invention particularly relates to an apparatus for protecting a horizontally reciprocable light projector from collision with a vertically reciprocable punch of a button setting machine, the button setting machine including a power-driven drive member, the light projector being normally disposed directly below the punch, said apparatus including first means for transmitting a driving power from the drive member to the light projector along a horizontal path, second means for transmitting a driving power from the drive member to the punch to reciprocate the punch along a vertical path, and mechanical means for producing a delay between retracting movement of the light projector and the downward movement of the punch to such an extent that the light projector is retracted from the vertical path of movement of the punch before the punch starts moving downward. US-A- 3 964 661 which forms the basis of present claim 1 disclosed an apparatus of the type mentioned above in which the drive member is formed by an air cylinder. In this conventional apparatus, at the end of every work hour, the apparatus stops and supply of compressed air is cut. At this very moment, a slide bar lies in the most advanced position and has placed an upper element at an upper station. A moment later, as the compressed air leaks gradually, the cylinder is urged against a block under the bias of a compression spring. Then, the slide bar comes to its most retracted position, leaving the upper element at an upper station. At this most retracted position, the slide bar has an ensuing upper element supplied from the chute set on itself. The next day, when the apparatus starts , the slide bar forces the ensuing element against the preceding element set on the upper station, thus causing the apparatus malfunction. In order to prevent this, the operator needs to manually take the preceding fastener out of the upper station whenever he may start the apparatus, which is very tedious and time-consuming. It is an object of the present invention to provide an apparatus for protecting a horizontally reciprocable light projector from collision with a vertical reciprocable punch which is immune from the disadvantage mentioned above. An apparatus satisfying this requirement is characterized in present claim 1. The above and other objects, features and advantages of the present invention will become manifest to those versed in the art upon making reference to the detailed description and the accompanying sheets of drawings in which preferred structural embodiments incorporating the principles of the present invention are shown by way of illustrative example. Figure 1 is a front elevational view, partly in cross section, of a button setting machine incorporating an apparatus for protecting an optical position indicator from collision with a punch of the button setting machine according to the present invention; Figure 2 is an enlarged cross-sectional view taken along line II - II of Figure 1; Figure 3 is a diagrammatical front elevational view showing the general construction of a collision protection apparatus according to another embodiment; Figure 4 is a view similar to Figure 3, but showing the construction of a modified collision protection apparatus; Figure 5 is a diagrammatical front elevational view showing a collision protection apparatus according to another embodiment; Figure 6 is a view similar to Figure 5, but showing a modified form of the collision protection apparatus; Figure 7 is a diagrammatical front elevational view showing the general construction of a collision protection apparatus according to still another embodiment of the invention; Figure 8 is a right side view of Figure 7; Figure 9 is a view similar to Figure 7, but showing a modified collision protection apparatus; Figure 10 is a right side view of Figure 9; Figure 11 is a diagrammatical front elevational view of a collision protection apparatus according to another embodiment of the invention; and Figure 12 is an enlarged view of a composite cam incorporated in the collision protection apparatus shown in Figure 11. Referring to the drawings, wherein like reference characters designate like or corresponding parts throughout the several views, and more particularly to Figure 1, there is shown a button setting machine for assembling upper and lower elements (not shown) of a garment fastener, such as a button, a stud button or a snap fastener, in clinched condition with a garment fabric sandwiched therebetween. The button setting machine includes an apparatus for protecting an optical indicator composed of a light projector from collision with a punch of the button setting machine according to the present invention. The button setting machine includes a punch 1 for forcing the upper fastener element into clinching engagement with the lower fastener element. The punch 1 is reciprocable vertically with respect to a frame 2 of the button setting machine. A die 3 is supported by the frame 2 directly below the punch 1 for holding thereon the lower fastener element. The punch 1 and the die 3 cooperate with each other to clinch the upper and lower fastener elements with a garment fabric disposed therebetween. The die 3 is connected at its lower end to one end of a lever 4 which is connected at its opposite end to a shock absorber (not shown) for taking up or absorbing a shock force applied to the die 3 when the upper and lower fastener elements are clinched together. The button setting machine further includes an upper pusher 5 for receiving an upper fastener element at a time from an upper chute 6 and for supplying the upper fastener element to an upper pocket or holder (not shown) disposed immediately below the punch 1 for holding the upper fastener element. The upper pusher 5 is pivoted to an upper pusher lever 7 so that it is movable alternately back and forth along a horizontal path in response to the pivotal movement of the upper pusher lever 7. The upper pusher 5 carries on its under side an optical position indicator 8 for indicating a position of the garment fabric where the upper and lower fastener elements are to be attached. The optical position indicator 8 comprises a light projector. A lower pusher 9 is movably supported on the frame 2 for receiving a lower fastener element at a time from a lower chute 10 and for supplying the lower fastener element to the die 3. The lower pusher 9 is pivoted to a lower pusher lever 11 and horizontally reciprocable in response to the pivotal movement of the lower pusher lever 11. The lower pusher lever 11 is urged by a tension coil spring 11a to turn counterclockwise in Figure 1 for normally holding the lower pusher 9 in its fully advanced position. When the lower pusher 9 is fully retracted, the forward end of the lower pusher 9 is disposed behind (left side in Figure 1) the lower end of the lower chute 10. The punch 1, the upper pusher 5 including the light projector 8, and the lower pusher 9 are all driven by a common drive unit including a fly wheel 12 continuously rotated by an electric motor via a V-belt (neither shown). A radial disk cam 13 is concentrically mounted on a central shaft of the fly wheel 12 via a single-revolution clutch (not shown). The single-revolution clutch is engaged to connect the continuously rotating fly wheel 12 and the cam 13 when a foot pedal (not shown) is depressed. When the cam 13 completes one revolution, the single-revolution clutch is disengaged to separate the cam 13 from the continuously rotating fly wheel 12. The cam 13 has an eccentric pin 14 projecting from an end face thereof and pivoted to a lower end of a crank lever 15. The crank lever 15 is directly connected at its upper end with a shaft 16 slidably received in a cylinder member 17. The shaft 16 has an actuator in the form of an annular flange 18 engageable with the lower end of the cylinder member 17. The actuating flange 18 is spaced a distance D from the lower end of the cylinder member 17 when the punch 1 is in its uppermost position. The upper end of the cylinder member 17 is pivoted to one end of a T-shaped lever 19, the opposite end of the T-shaped lever 19 being operatively connected to an upper end of the punch 1. The T-shaped lever 19 is pivotally movable about a shaft 20 to reciprocate the punch 1 vertically toward and away from the die 3. With this construction, when the cam 13 is driven to rotate, the shaft 16 immediately starts moving upwardly into the cylinder member 17. In this instance, however, due to the space D provided between the annular actuating flange 18 and the lower end of the cylinder member 17, pivotal movement of the T-shaped lever 19 does not occur until the annular actuating flange 18 on the shaft 16 abuts against the lower end of the cylinder member 17. Thus, the shaft 16 and the cylinder member 17 jointly constitute a lost motion mechanism 21 which produces the lost motion or the delay between the movement of a driver (cam 13 in the illustrated embodiment) and the movement of a follower (the T-shaped lever 19 in the illustrated embodiment). A vertical cam lever 22 is pivotally connected at its lower end to a horizontal shaft 24 secured to the frame 2 and has a roller follower 23 rollingly engageable with a cam surface 13a of the cam 13. When cam 13 rotates, the cam lever 22 angularly oscillates about the shaft 24. The cam lever 22 is normally urged by a tension coil spring 25 in a direction to keep the roller follower 23 in contact with the cam surface of the cam 13. The cam lever 22 is pivoted at its upper end portion to one end of a horizontal actuating rod 26, the opposite end of the actuating rod 26 being connected with the upper pusher lever 7. The connection between the actuating rod 26 and the upper pusher lever 7 is such that a small-diameter end portion 26a of the actuating rod 26 is slidably received in a hole in a bearing 7a provided on the upper pusher lever 7, as shown in Figure 2. The T-shaped lever 19 has a vertical arm 30 extending downwardly from a substantially central portion of the lever 19 and pivotally connected at its distal end to one end of an expansion pipe joint 31. The opposite end of the expansion pipe joint 31 is pivoted to the lower pusher lever 11 adjacent to an upper end thereof. The expansion pipe joint 31 is composed of an outer pipe 32 connected to the arm 30 and an inner pipe 33 connected to the lower pusher lever 11 and slidably received in the outer pipe 32. With the expansion pipe joint 31 thus provided, only the pivotal movement of the T-shaped lever 19 in the clockwise direction is transmitted to the lower pusher lever 11 while the pivotal movement of the T-shaped lever 19 in the counterclockwise direction has no effect on the movement of the lower pusher lever 11. When the T-shaped lever 19 turns counterclockwise about the shaft 20, the lower pusher lever 11 follows the angular movement of the T-shaped lever 19. However, this angular movement of the lower pusher lever 11 is caused by the force of the tension coil spring 11a and does not result from pivotal movement of the T-shaped lever 19. Consequently, when a lower fastener element jams as it is fed by the lower pusher 9 toward the die 3, advancing movement of the lower pusher 9 is interrupted by the jamming lower fastener element. If the T-shaped lever 19 and the lower pusher lever 11 are directly connected together, the lower pusher lever 11 is forced by the T-shaped lever 19 to turn counterclockwise, thereby forcibly advancing the lower pusher 9 even when jamming of the lower fastener element takes place. Such forcible feeding of the jamming fastener element would damage the button setting machine. A tension coil spring 27 acts between the lower pusher lever 11 and the lower pusher 9 to urge the latter slightly upwardly so as not to sink the forward end of the lower pusher 9. Likewise, a tension coil spring 28 acts between the upper pusher lever 7 and the upper pusher 5 to urge the latter slightly upwardly for holding the horizontal posture of the upper pusher 5. A stopper 29 is disposed behind the upper pusher lever 7 and engageable with the same to limit backward or retracting movement of the upper pusher 5. The stopper 29 comprises a stop bolt and hence is adjustable in position so that the backward stroke of the upper pusher 5 can be adjusted. The upper pusher lever 7 is urged by a tension coil spring 34 to turn clockwise toward the stopper 29. The upper pusher lever 7 is turned counterclockwise against the force of the tension coil spring 34 when the actuating rod 26 is advanced toward the upper pusher lever 7. Due to the loose fitting connection between the small-diameter end portion 26a of the actuating rod 26 and the bearing 7a on the upper pusher lever 7, retracting movement of the actuating rod 26 permits the upper pusher lever 7 to turn clockwise under the force of the tension coil spring 34, thereby retracting the upper pusher 5 and the light projector 8. The button setting machine of the foregoing construction operates as follows. For purposes of illustration, operation of the button setting machine begins from a condition shown in Figure 1 where the punch 1 is fully retracted, while the upper and lower pushers 5, 9 are fully advanced so that an upper fastener element is held by the upper holder below the punch 1 and a lower fastener element is placed on the die 3. The light projector 8 mounted on the upper pusher 5 assumes its advanced position. When a start switch (not shown) of the button setting machine is turned on, the motor-driven fly wheel 12 rotates continuously. In this instance, the single-revolution clutch is in the disengaged state so that the rotational movement of the fly wheel 12 is not transmitted to the cam 13. The light projector 8 projects a light beam passing along a common vertical axis of the punch 1 and the die 3. The light beam produces a light spot on a garment fabric when the latter is disposed between the light projector 8 and the die 3. After a position on the garment fabric where the upper and lower fastener elements are to be attached has been set in registry with the light spot, a foot pedal is depressed whereupon the single-revolution clutch is engaged to connect the continuously rotating fly wheel 12 and the cam 13, thereby rotating the cam 13 in the clockwise direction as indicated by the arrow shown in Figure 1. The clockwise movement of the cam 13 causes the roller follower 23 to relatively move from a flat cam surface to an arcuate cam surface 13a so that the cam lever 22 is turned counterclockwise about the shaft 24 against the force of the tension coil spring 25. With this counterclockwise movement of the cam lever 22, the actuating rod 26 is retracted whereupon the upper pusher lever 7 is permitted to turn clockwise under the force of the tension coil spring 34 until it assumes its fully retracted position indicated by the phantom lines. As a result, the upper pusher 5 and the light projector 8 mounted thereon are retracted away from a vertical path of movement of the punch 1. The retracting movement of the upper pusher 5 and the light projector 8 is completed before the cam 13 advances through an angular distance which is equivalent to a linear advancing movement of the shaft 16 over the distance D (i.e., the lost motion) provided by the lost motion mechanism 21. With the action of the lost motion mechanism 21, the T-shaped lever 19 is kept immovable so that downward movement of the punch 1 never occurs before the upper pusher 5 and the light projector 8 are fully retracted. A continuing clockwise movement of the cam 13 causes the eccentric pin 14 to further advance the shaft 16 into the cylinder member 17 whereupon the annular actuating flange 18 on the shaft 16 is brought into abutment with the lower end of the cylinder member 17. Thereafter, the shaft 16 and the cylinder member 17 move upwardly in unison with each other against the force of a tension coil spring 35 so that the T-shaped lever 19 is turned about the shaft 20 in the clockwise direction to thereby lower the punch 1 toward the die 3. When the cam 13 has advanced through an angle of 180 degrees, the eccentric pin 14 is disposed in its uppermost position and the punch 1 is fully advanced. The upper and lower fastener elements are thus attached to the garment fabric accurately at the desired position. As the cam 13 further continues its clockwise movement, the eccentric pin 14 moves from its uppermost position toward its lowermost position. Consequently, the cylinder member 17 is lowered by the force of the tension coil spring 35 whereby the T-shaped lever 19 is turned counterclockwise to thereby retract the punch 1 upwardly away from the die 3. The downward movement of the cylinder member 17 is limited to such an extent that the distance D is provided between the annular actuating flange 18 and the lower end of the cylinder member 17 when the eccentric pin 14 is disposed in its lowermost position. In the illustrated embodiment, the downward movement of the cylinder member 17 is limited by a stopper 44 which is provided on the frame 2 and engageable with the T-shaped lever 19 to limit its pivotal movement in the counterclockwise direction. When the cam 13 completes a single revolution, the single revolution clutch is disengaged to thereby separate the cam 13 from the continuously rotating fly wheel 12. In this instance, the cam 13 is disposed in its initial position and hence the cam lever 22 is turned about the shaft 24 clockwise by the force of the tension coil spring 25. The clockwise movement of the cam lever 22 advances the actuating rod 26 to turn the upper pusher lever 7 counterclockwise, thereby advancing the upper pusher 5 and the light projector 8 into a position directly below the punch 1. As described above, the punch 1 descends only after the upper pusher 5 and the light projector 8 are fully retracted away from the vertical path of movement of the punch 1. Accordingly, collision or accidental interference between the light projector 8 and the punch 1 can be completely avoided even when the light projector 8 is disposed near the lower end of the punch 1. With this timed relation between the movement of the punch 1 and the movement of the light projector 8, the provision of the light projector 8 does not increase the stroke of the punch 1 and hence the overall size of the button setting machine is relatively small. The distance D between the annular actuating flange 18 on the shaft 16 and the lower end of the cylinder member 17 may be selected in such a manner that the distance D becomes zero (D = 0) and hence the downward movement of the punch 1 begins at a moment when the light projector 8 is rearwardly offset from the vertical path of movement of the punch 1. Figure 3 diagrammatically shows a portion of the button setting machine having a collision protection apparatus according to another embodiment of the present invention. The collision protection apparatus is similar to the apparatus shown in Figure 1 but differs therefrom in that the punch 1 is pivoted at its upper end to one lever of a toggle joint 40, and that the cylinder member 17 of a lost motion mechanism 21 is pivotally connected at its upper end to one end of a L-shaped lever or bell-crank 41, the opposite end of the bell-crank 41 being connected with the toggle joint 40 via a link 42. As the cam 13 is rotated clockwise as indicated by the arrow, the cam lever 22 is pivoted leftward to thereby retract the light projector 8 attached to the upper pusher 5, then the cylinder member 17 moves upwardly to turn the bell-crank 41 clockwise about a shaft 43 whereupon the toggle joint 40 is expanded by the link 42 to thereby lower the punch 1. Likewise the embodiment shown in Figure 1, the retracting movement of the light projector 8 begins while the punch 1 is at rest in the uppermost position, and the downward movement of the punch 1 is started after the light projector 8 is retracted from the vertical path of movement of the punch 1. Accordingly, the light projector 8 is protected from collision with the punch 1. Designated by 44 is a stopper engageable with the bell-crank 41 to provide a distance D between the annular actuating flange 18 and the cylinder member 17, that is, the delay between the retracting movement of the light projector 8 and the downward movement of the punch 1. The distance D becomes zero (D = 0) and hence the downward stroke of the punch 1 begins when the light projector 8 is retracted from the vertical path of movement of the punch 1. A modified collision protection apparatus shown in Figure 4 is substantially the same as the apparatus shown in Figure 1 with the exception that the cam 13 is a composite cam having a first cam surface 50 profiled to retract the light projector 8, and a second cam surface 51 profiled to vertically reciprocate the punch 1, the first cam surface 50 being eccentric to the axis of rotation of the cam 13 and the second cam surface 51. When the cam 13 is rotated in the direction of the arrow, the first cam surface 50 urges the roller follower 23 outwardly (leftward in Figure 4). The cam lever 22 is therefore turned counterclockwise about the shaft 24 to thereby retract the actuating rod 26. In response to the retracting movement of the actuating rod 26, the upper pusher lever 7 is turned in the clockwise direction by the force of the tension coil spring 34 so that the light projector 8 is retracted from the vertical path of movement of the punch 1. The second cam surface 51 has an approximately pear-shaped profile having a circular curve of a constant radius of curvature which is concentric with the axis of rotation of the cam 13 and extends over a substantial part of the full circumference of the cam profile. A portion of the second cam surface having the constant radius of curvature continuously engages a roller follower 52 until the cam 13 moves through a predetermined angular distance a . During that time, a camming action tending to lift a vertically slidable connecting rod 53 is not imparted from the second cam surface 51 to the roller follower 52. As a result, the T-shaped lever 19 is kept immovable and hence the punch 1 is held in its uppermost position. The downward movement of the punch 1 begins when the angular movement of the cam 13 exceeds the predetermined angular distance a . Thus, the first and second cam surfaces 50, 51 are arranged in such a relation that the predetermined angular distance a introduces a pause of a desired length into the motion of the connecting rod 53 and hence the motion of the punch 1. The length of the pause in motion corresponds to the delay between the retracting movement of the light projector 8 and the downward movement of the punch 1 which is produced by the distance D provided by the lost motion mechanism 21 described with respect to the foregoing embodiments shown in Figures 1 and 3. Thus, the second cam surface 51 and the connecting rod 53 having the roller follower 52 jointly constitutes a modified delay producing mechanism. The upward movement of the punch 1 is achieved by the force of a tension coil spring 54 acting on the T-shaped lever 19. Figure 5 shows a portion of the button setting machine incorporating a collision protection apparatus according to a fourth embodiment of the present invention. The collision protection apparatus is similar to the apparatus shown in Figure 1 but differs therefrom in the construction of a lost motion mechanism. In this embodiment, the lost motion mechanism includes an elongate vertical lever 60 having an oblong hole 61 extending longitudinally along an upper end portion of the vertical lever 60, and a pin 62 movably received in the oblong hole 60 and connected to one end of the T-shaped lever 19. The oblong hole 61 has a length D which is equal to the distance D provided by the lost motion mechanism 21 shown in Figure 1. With this construction, the cam 13 is rotated in the direction of the arrow whereupon the cam lever 22 is caused to turn about the shaft 24 in the counterclockwise direction. This pivotal movement of the cam lever 22 causes the light projector 8 to retract from the vertical path of movement of the punch 1 under the force of the tension coil spring 34. During that time, the vertical lever 60 is lifted, however, the upward movement of the vertical crank lever 60 is not transmitted to the T-shaped lever 19 because the pin 62 simply slides along the oblong hole 61 in the crank lever 60. The pivotal movement of the T-shaped lever 19 tending to lower the punch 1 begins when the pin 62 engages a lower end edge of the oblong hole 61. The pin 62 is normally held in contact with the upper end edge of the oblong hole 61 by a stopper 44 acting on the T-shaped lever 19. The length D of the oblong hole 61 is selected such that the pin 62 is brought into engagement with the lower end edge of the oblong hole 61 to thereby turn the T-shaped lever 19 clockwise for lowering the punch 1 when the light projector 8 is retracted from the vertical path of movement of the punch 1. A modified collision protection apparatus shown in Figure 6 includes a rotating circular disk 70 driven by a power-driven fly wheel (see Figure 1), and an elongate vertical lever cam 71 operatively connected at its lower end to an eccentric pin 14 secured to the circular disk 70. The lever cam 71 has an oblong hole 61 extending longitudinally along an upper end portion thereof and movably receiving therein a pin 61 connected to one end of the T-shaped lever 19, and a cam surface 71a extending along a length of one longitudinal edge of the lever cam 71 and acting on a roller follower 72 mounted on one end of a bell-crank 73. The other end of the bell-crank 73 is pivotally connected to an end of the actuating rod 26. With this construction, when the circular disk 70 is rotated in the direction of the arrow, the lever cam 71 moves vertically upwardly. The upward movement of the lever cam 71 causes the roller follower 72 to ride on the cam surface 71a whereupon the bell-crank 73 is turned clockwise to thereby retract the light projector 8 from the vertical path of movement of the punch 1 under the force of the tension coil spring 34. During that time, the punch 1 is kept immovable due to the action of the lost motion mechanism formed jointly by the oblong hole 61 and the pin 62 slidably received therein. A continuing upward movement of the lever cam 71 causes the lower end edge of the oblong hole 61 to engage the pin 62 and then turn the T-shaped lever 19 in the clockwise direction, thereby lowering the punch 1. The length of the oblong hole 61 is selected such that the engagement of the lower end edge of the oblong hole 61 and the pin 62 occurs when the light projector 8 is retracted from the vertical path of movement of the punch 1. Figures 7 and 8 diagrammatically illustrate a collision protection apparatus according to a sixth embodiment of the present invention. The apparatus includes an L-shaped lever 81 pivotally movable about a horizontal shaft 82. The L-shaped lever 81 carries on its upper end a roller follower 80 engageable with a cam surface 13a of the rotating cam 13 and is pivotally connected to the upper pusher 5. In response to the rotation of the cam 13, the L-shaped lever 81 turns clockwise to thereby retract the light projector 8 from the vertical path of movement of the punch 1. The cam 13 has an eccentric pin 14 connected to an upper end of a crank 15. The lower end of the crank 15 is connected with a cylinder member 17 which slidably receives a shaft 83 projecting outwardly from an upper end of the punch 1. The upper end of the punch 1 is normally spaced from the cylinder member 17 by a distance D. To this end, a stopper 44 is provided to limit the upward movement of the punch 1 as the punch is lifted by the force of a tension coil spring 35. The cylinder member 17 and the shaft 83 thus spaced jointly constitute a lost motion mechanism which provides the delay between the retracting movement of the light projector 8 and the downward movement of the punch 1. With this lost motion mechanism, a start of the downward movement of the punch 1 is retarded until the cylinder member 17 impinges upon the upper end of the punch 1, in which instance the light projector 8 is rearwardly offset from the vertical path of movement of the punch 1. Since the cylinder member 17 and the L-shaped lever 81 are directly connected with the punch 1 and the upper pusher 5, respectively, the button setting machine of this embodiment is simpler in construction than the button setting machine of any of the foregoing embodiments. Figures 9 and 10 show a modified form of the collision protection apparatus according to the present invention. The modified apparatus is substantially the same as the apparatus shown in Figures 7 and 8, excepting that the lost motion mechanism is composed of an oblong hole 91 formed longitudinally in an elongate vertical connecting member 90 pivotally connected to the crank 15, and a horizontal pin 92 extending transversely across an recessed upper end portion of the punch 1 and slidably received in the oblong hole 91. When the cam 13 is rotated, the connecting member 90 is moved downwardly, however, due to the lost motion mechanism, the downward movement of the connecting member 90 is not transmitted to the punch 1 until the upper end edge of the oblong hole 91 engages the pin 92 on the punch 1. During that time, the L-shaped lever 81 turns clockwise under the action of the cam surface 13a to thereby retract the light projector 8 from the vertical path of movement of the punch 1. As the connector member 90 further moves downward, the upper end edge of the oblong hole 91 is brought into engagement with the pin 2 and then urges the pin 92 downwardly to thereby lower the punch 1. Figures 11 and 12 diagrammatically show a part of a button setting machine incorporating a modified collision protection apparatus according to another embodiment of the present invention. The apparatus is similar to the apparatus shown in Figures 7 and 8 but differs therefrom in that the cam 13 is a composite cam including a first cam surface 100 having a cam profile which is capable of oscillating the L-shaped lever 81 via the roller follower 80 for retracting the light projector 8 from the vertical path of movement of the punch 1, and a second cam surface 100 concentric with the first cam surface 101 and having a cam profile which is capable of lowering the punch 1 via a roller follower 102 rotatably mounted on an upper end of the punch 1. When the cam 13 is rotated in either direction, the roller follower 80 on the L-shaped lever 81 rides on the first cam surface 100, thereby causing the L-shaped lever 81 to pivot in a direction to retract the light projector 8 from the vertical path of movement of the punch 1. During that time, the roller follower 102 on the punch 1 rolls along a portion of the second cam surface 101 which has a cam profile of a constant radius of curvature. Consequently, the second cam surface 101 does not produce a camming action tending to lower the punch 1. As the angular movement of the cam 13 further advances, the second cam surface 101 urges the roller follower 102 downwardly to thereby lower the punch 1. Thus, the first and second cam surfaces 100, 101 are so profiled as to create the delay between the retracting movement of the light projector 8 and the downward movement of the punch 1. The punch 1 is returned to its uppermost position under the force of the tension coil spring 103. The radial disk cam 13 may be substituted by a face cam having first and second cam surfaces on its one side. As an alternative, a face cam having two grooves in its opposite surfaces may be employed in place of the radial disk cam 13.

Claims: An apparatus for protecting a horizontally reciprocable light projector (8) from collision with a vertically reciprocable punch (1) of a button setting machine, the button setting machine including a power-driven drive member (12), the light projector (8) being normally disposed directly below the punch (1), said apparatus including first means (13; 22; 70-73; 81) for transmitting a driving power from the drive member (12) to the light projector (8) to reciprocate the light projector (8) along a horizontal path, second means (19; 41; 53; 102) for transmitting a driving power from the drive member (12) to the punch (1) to reciprocate the punch (1) along a vertical path, and mechanical means (21; 50; 51; 100; 101) for producing a delay between retracting movement of the light projector (8) and the downward movement of the punch (1) to such an extent that the light projector (8) is retracted from the vertical path of movement of the punch (1) before the punch (1) starts moving downward. characterized in that said drive member is a continuously rotating fly wheel (12) and that said first and second power transmitting means comprise a rotating member (13; 70) operatively connected with said fly wheel (12) via a single revolution clutch. An apparatus according to claim 1, wherein said first power transmitting means includes a cam (13) rotated by the rotating drive member (12) and a pivotable cam lever (22) operatively connected with the light projector (8) and driven by said cam (13) to reciprocate the light projector (8) toward and away from the vertical path of movement of the punch (1), said second power transmitting means including a crank mechanism (14, 15; 60) operatively connected with the punch (1) and said cam (13) and driven by said cam (13) to reciprocate the punch (1) along the vertical path, said delay-producing mechanical means including a lost motion mechanism (21) incorporated in said crank mechanism (14, 15; 60). An apparatus according to claim 2, wherein said second power transmitting means further includes a lever (19; 41) having one end operatively connected with the punch (1) and an opposite end connected to said crank mechanism (14, 15). An apparatus according to claim 3, wherein said second power transmitting means further includes a toggle joint (40) having two bars pivoted together at one end, one of said bars being connected at its opposite end to the punch (1), said lever (41) comprising a bell-crank having one end operatively connected to a pivot of said toggle joint (40). An apparatus according to claim 2, wherein said crank mechanism includes a crank (15) connected at its one end to said cam (13) by an eccentric pin (14), said lost motion mechanism (21) including a shaft (16) extending from an opposite end of said crank (15) and having an annular actuating flange (18), and a cylinder member (17) connected to said opposite end of said lever (19; 41) and slidably receiving therein said shaft (16), said actuating flange (18) being normally separated from said cylinder member (17) and engageable with said cylinder member (17) to turn said lever (19; 41) in a direction to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1). An apparatus according to claim 3, wherein said crank mechanism includes an elongate crank lever (60) connected at its one end to said cam (13) by an eccentric pin (14), said lost motion mechanism (21) comprising an oblong hole (61) extending longitudinally in said crank lever (60) and a pin (62) slidably received in said oblong hole (61) and connected to the opposite end of said lever (19), said oblong hole (61) having one end edge normally separated from said pin (62) and engageable with said pin (62) to turn said lever (19) in a direction to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1). An apparatus according to claim 2, wherein said crank mechanism includes a crank (15) connected at its one end to said cam (13) by an eccentric pin (14), said lost motion mechanism (21) including a cylinder member (17) connected at one end to the opposite end of said crank (15) and a shaft (83) integral with an upper end of the punch (1) and slidably received in said cylinder member (17), said cylinder member (17) being normally separated from the upper end of the punch (1) and engageable with the upper end of the punch (1) to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1). An apparatus according to claim 2, wherein said crank mechanism includes a crank (15) connected at its one end to said cam (13) by an eccentric pin (14) and a connecting member (90) connecting the opposite end of the crank (15) and an upper end of the punch (1), said lost motion mechanism (21) comprises an oblong hole (91) extending longitudinally in said connecting member (90) and a pin (92) slidably received in said oblong hole (91) and connected to the upper end of the punch (1), said oblong hole (91) having one end edge normally separated from said pin (92) and engageable with said pin (92) to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1). An apparatus according to claim 1, wherein said first power transmitting means includes a circular disk (70) rotated by the rotating drive member (12), a lever cam (71) reciprocally driven by said circular disk (70) and having a cam surface (71a), and a bell-crank (73) having one end operatively connected with the light projector (8) and the opposite end co-acting with said cam surface (71a) to turn said bell-crank (73), said second power transmitting means including a lever (19) operatively connected at its one end with the punch (1) and at its opposite end with said lever cam (71), said delay producing mechanical means including a lost motion mechanism (21) composed of an oblong hole (61) extending longitudinally in said cam lever (71) and a pin (62) slidably received in said oblong hole (61) and connected to said opposite end of said lever (19), said oblong hole (61) having one end edge normally separated from said pin (62) and engageable with said pin (62) to turn said lever (19) in a direction to lower the punch (1) when the light projector (8) is retracted from the vertical path of movement of the punch (1). An apparatus according to claim 1, wherein said first power transmitting means includes a composite cam (13) rotated by the rotating drive member (12) and having first and second cam surfaces (50, 51), and a pivotable cam lever (22) operatively connected with the light projector (8) and driven by said first cam surface (50) of said composite cam (13) to reciprocate the light projector (8) toward and away from the vertical path of movement of the punch (1), said second power transmitting means including a lever (19) operatively connected at its one end with the punch (1) and a reciprocable connecting rod (53) having one end connected with the opposite end of said lever (19) and the opposite end co-acting with said second cam surface (51) to turn said lever (19) for reciprocating the punch (1), said delay producing mechanical means comprising said first and second cam surfaces (50, 51), said first and second cam surfaces (50, 51) having respective cam profiles capable of producing said delay between the retracting movement of the light projector (8) and the downward movement of the punch (1). An apparatus according to claim 1, wherein said first power transmitting means includes a composite cam (13) rotated by the rotating drive member (12) and having first and second cam surfaces (100, 101), and a pivotable cam lever (81) operatively connected with the light projector (8) and driven by said first cam surface (100) of said composite cam (13) to reciprocate the light projector (8) toward and away from the vertical path of movement of the punch (1), said second power transmitting means including a cam follower (102) rotatably mounted on an upper end of the punch (1) and co-acting with said second cam surface (101) to move the punch (1) downward, said delay producing mechanical means comprising said first and second cam surfaces (100, 101), said first and second cam surfaces (100, 101) having respective cam profiles capable of producing said delay between the retracting movement of the light projector (8) and the downward movement of the punch (1).

Inventors: SODENO TOSHIAKI, TOISHI YOSHIYUKI, SODENO, TOSHIAKI, TOISHI, YOSHIYUKI
Applicants: YOSHIDA KOGYO KK, YOSHIDA KOGYO K.K.
Application year: 1990
Main classification: A41H37
IPC codes: A44B17, A41H37, F16P7