APPARATUS FOR ASSEMBLING PAIRS OF GARMENT FASTENER ELEMENTS

Abstract: A garment-fastener assembling apparatus includes a combined supporting and connecting mechanism composed of a pivot lever (79) rotatably mounted on a frame (20) and pivotably connected at its one end with the cylinder tube of a punch-driving cylinder (72) and at the other end with a first pusher mechanism (28) having a first pusher (85), and a spring-biased slide rod (93) slidably mounted on the frame and having one end pivoted to the pivot lever adjacent to the cylinder tube. The slide rod is normally urged such that during a portion of the movment of the piston rod (77) from the cylinder tube adjacent to the fully retracted position of the piston rod, the pivot lever operates the first pusher mechanism to retract and advance the first pusher. With the combined mechanism thus constructed, a punch (27) and the first pusher can be driven in an acculate timed relation to one another. The first pusher mechanism includes a chshioning arrangement (8l, 84, 86, 88) for preventing advancing movment of the first pusher (85) if an element-feed passage (37) is jammed by a foreign matter. The stroke of a second pusher (l40) can be adjusted independently from the stroke of a die (3l) by a cam block (l69) connected to the piston rod (l68) of a die-driving cylinder (l64).

Description: The present invention relates to an apparatus for assembling a pair of fastener elements of a garment fastener, such as a button, a snap button or an ornament, with a garment fabric disposed between the two fastener elements. U.S. Patent No. 3,964,66l, issued June 22, l976 discloses a fastener-assembling apparatus which includes a first drive mechanism for vertically reciprocating an upper punch of an upper unit, a second drive mechanism for vertically reciprocating a lower punch or die of a lower unit, a first pusher mechanism having an upper pusher reciprocally driven by the first drive mechanism to supply one of a pair of fastener elements to the upper unit, a second pusher mechanism having a lower pusher reciprocally driven by the second drive mechanism to supply the other fastener element to the lower unit, and an indicator fixedly connected to the upper pusher for directing a beam of light to a garment fabric to indicate a position on the garment fabric where the two fastener elements are to be attached. The drive and pusher mechanisms are operatively linked with each other in such a manner that the upper and lower pushers are retracted from the path of movement of the punch and die in response to the movement of the punch and die in a direction toward each other to clinch the two fastener elements together, with the garment fabric sandwiched between the fastener elements. The known apparatus of the foregoing construction has various drawbacks, as follows: The first drive mechanism includes a cylinder slidably supported on the frame and operatively connected with the first pusher mechanism. However, there is no direct connection between suppoting means and connecting means with the result an accurate timed operation of the first drive mechanism and the first pusher mechanism is difficult to achieve. Furthermore, the upper pusher of the first pusher mechanism is operatively connected with the cylinder of the first drive mechanism through a pair of pivot levers linked together with a compression coil spring acting therebetween. When a cylinde tube of the cylinder is axially moved in a direction to advance the upper pusher, the spring-biased pivot levers resiliently move the upper pusher forwardly, thereby preventing abrupt supply of the fastener element to the upper unit. The spring-biased levers, however, do not change the direction of power transmission path extending from the cylinder tube to the upper pusher with the result that the upper pusher is forced to advance the fastener element even when a foreign matter is present in an element-feed path. With this forcible feeding, the fastener element is likely to be damaged or otherwise deformed. Another problem is that the cylinder is slidably supported on a block secured to a frame and is urged by a spring against the block. Upon energization and de-energization of the cylinder, the cylinder tube hits against the block, thereby generating objectionable shock noises and vibration. It is a further drawback of the known apparatus that the lower pusher and the die are reciprocated by a single cylinder via a linkage mechanism. Both the stroke of the lower pusher and the stroke of the die are depending on the stroke of the cylinder and hence a separate stroke adjustment of the lower pusher and the die is difficult to achieved. With this difficulty, a reliable attachment can not be expected when the fastener elements are to be set on garment fabrics varying in thickness. Another difficulty is that the position indicator is structurally and operatiionally integral with the upper pusher and hence requires a relatively large operating area. The position indicator is retracted from the path of movement of the punch upon actuation of the air cylinder to lower the punch. It is therefore no longer possible for the operator to monitor as to whether the fastener elements are being set on the garment fabric accurately at the desired position. Further, the indicator has a downwardly projecting portion which would catch a garment fabric as the indicator reciprocates in unison with the upper pusher. A still further problem is that the known apparatus has no means for retaining an upper unit reliably in a position to receive the fastener element from the upper pusher. Rather, the upper unit is likely to be displaced from the element-receiving position when the stroke of the punch is changed while in use. Furthermore, the prior apparatus requires a tedious and time-consuming operation for removing a foreign matter or a jamming fastener element from the feed path, resulting in downtime of the apparatus. With the foregoing drawbacks of the prior art in view, a general object of the present invention is to provide a garment-fastener assembling apparatus so constructed as to enable a stable and reliable assembling of a pair of fastener elements of a garment fastener with a garment fabric sandwiched between the two fastener elements. The present invention seeks to provide an apparatus having structural features which ensure that a clinching operation and a fastener-element supply operation can be achieved in an accutate timed relation to one another. The present invention further seeks to provide a fastener-assembling apparatus which includes a first pusher mechanism so constructed as to protect fastener elements against damage even when a foreign matter is present in an element-feed path. The present invention further seeks to provide a fastener-assembling apparatus having a shock absorber associated with a drive cylinder for preventing generation of objectionable shock noises and vibration. The present invention further seeks to provide a fastener-assembling apparatus, in which a second pusher mechanism is capable of feeding fastener elements stably even when pairs of fastener elements are to be attached to garment fabrics of different thicknesses. The present invention further seeks to provide a fastener-assembling apparatus including an optical position indicator which requires only a limited operating space, does not interfere positioning of a garment fabric with respect to a punch and die assembly, and enables the operator to monitor the setting condition of the garment fabric until the upper unit comes close to the position indicator. The present invention further seeks to provide a fastener assembling apparatus having a retainer for holding an upper unit stably and accurately in an element-receiving position. The present invention further seeks to provide a fastener-assembling apparatus including means for removing a foreign matter or a jamming fastener element from an element-feed path. According to the present invention, there is provided an apparatus for assembling a pair of fastener elements of a garment fastener with a garment fabric disposed between the two fastener elements, comprising: a frame; a pair of vertically aligned upper and lower units supported by said frame for receiving the respective fastener elements, said upper unit having a punch, said lower unit having a die, said punch and said die being reciporcably movable toward and away from each other to join the two fastener elements together with the garment fabric sandwiched therebetween; a first drive mechanism for reciprocating said punch, said first drive mechanism including a fluid-pressure actuator having a piston rod and a cylinder tube; a first pusher mechanism including first means supported by said frame and defining a first feed passage receptive of one fastener element, said first pusher mechanism also including a first pusher reciprocable within said first feed passage to push the one fastener element therethrough to said upper unit; a second drive mechanism for reciprocating said die; and a second pusher mechanism including second means supported by said frame and defining a second feed passage receptive of the other fastener element, said second pusher mechanism also including a second pusher reciprocable within said second feed passage to push the other fastener element therethrough to said lower unit; characterized by a combined supporting and connecting mechanism for slidably and pivotably supporting said fluid-pressure actuator on said frame and also for operatively connecting said fluid-pressure actuator and said first pusher mechanism, said combined mechanism including a pivot lever rotatably mounted on said frame and pivotably connected at opposite ends with said cylinder tube and said first pusher mechanism, and a spring-biased slide rod slidably mounted on said frame and pivotably connected at its one end to said pivot lever adjacent to said cylinder tube, said slide rod being normally urged in a direction such that during a portion of the movement of said piston rod from said cylinder tube adjacent the fully retracted position of said piston rod, said pivot lever operates said first pusher mechanism to retract and advance said first pusher. With the combined supporting and connecting mechanism thus constructed, a punch and the first pusher can be operated in accurate timed relation to one another. The first pusher mechanism includes a cushioning rod pivoted at its one end to the other end of the pivot lever, a pivotable actuating lever pivoted at its one end to a rear end of the first pusher, a tubular connecting bar pivotably connected at one end to the other end of the actuating lever and loosely receiving the cushioning rod from the other end thereof, a presser member disposed on the cushioning rod and engageable with the other end of the connecting bar, and biasing means disposed in the tubular connecting bar and acting between the connecting bar and the cushioning rod for urging the latter in a direction to keep the presser member in engagement with the other end of the connecting rod. With this first pusher mechanism, a damage-free feeding of one fastener element by the first pusher is achieved even when a foreign matter is jamming an element-feed passage. The spring-biased slide rod includes a flange engageable with the frame to limit movement of the slide rod in one direction. A shock absorber is cooperative with the slide rod to absorb shock noise and vibration when the flange engages the frame. The shock absorber preferably includes a dashpot and a resiliently deformable cushioning ring. The apparatus also includes a retainer mechanism incorporated in a punch-driving ram and lockingly engageable with an element-supporting holder for retaining an element-supporting portion of the holder in an element-receiving position when the punch is in its uppermost standby position. A gate unit is supported on the frame and includes a slide block extending along a first feed feed passage along which one fastener is fed. The slide block is movable in a direction parallel to the first feed passage between a first position in which the slide block is disposed in confronting relation to the discharge end of an element-supplying chute so as to define therebetween the first feed passage, and a second position in which the slide block is disposed out of confrontation with the discharge end, the slide block being normally held in the first position. If the first feed passage is jammed by a foreign matter or the fastener element, the slide block is brought to the second position to enable removal of the jamming substance. The apparatus further includes an optical position indicator movably supported by the frame for indicating a position on a garment fabric where two fastener elements are to be attached, and a drive mechanism operatively connected with the position indicator and movable under the control of the first pusher mechanism for reciprocating the position indicator toward and away from the path of movement of the punch in such a manner that retracting movement of the position indicator begins slightly after the start of retracting movement of the first pusher. With the delay in motion thus provided, the stroke of the position indicator is relatively short and an additional period of time is available for monitoring the position setting of the garment until the upper unit comes close to the position indicator. A drive mechanism for reciprocating a die includes a fluid-pressure actuator having a piston rod. A second pusher mechanism for reciprocating a second pusher includes a cam block connected to the piston rod of the drive mechanism, and a pivot lever urged against a cam surface on the cam block and operatively connected to the second pusher for reciprocating the latter in response to the reciprocating movement of the piston rod. The cam surface is profiled such that during a portion of movement of the piston rod from the actuator adjacent the fully retracted position of the piston rod, the cam surface turns the pivot lever to reciprocate the second pusher, while during a portion of movement of the piston rod from the actuator adjacent the fully extended position of the piston rod, the cam surface does not turn the pivot lever to interrupt reciprocating movement of the second pusher. With the cam block thus constructed, the stroke of the second pusher is independent from the stroke of a die and hence a proper clinching of the two fastener elements can be achieved even when the garment fabric varies in thickness. Many other advantages and features 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 a preferred structural embodiment incorporating the principles of the present invention is shown by way of illustrative example. Figure l is a schematic front elevational view showing the general construction of a fastener-assembling apparatus embodying the present invention; Figure 2 is a front elevational view, partly in cross section, of a pair of fastener elements to be joined together by the apparatus shown in Figure l; Figure 3 is an enlarged front elevational view, partly in cross section, of an upper part of the apparatus of Figure l; Figure 4 is an enlarged left side view of a portion of Figure 3; Figure 5 is an enlarged cross-sectional view taken along line V-V of Figure 3; Figure 6 is an enlarged front elevational view of a portion of the upper part shown in Figure 3, illustrating a position-indicator driving mechanism and a gate unit; Figure 7 is a cross-sectional view taken along line VII-VII of Figure 6; Figure 8 is a cross-sectional view taken along line VIII-VIII of Figure 6; Figure 9 is a cross-sectional view taken along line IX-IX of Figure 6; Figure l0 is an enlarged front elevational view, partly in cross section, of a lower part of the apparatus shown in Figure l; Figure ll is an enlarged cross-sectional view taken along line XI-XI of Figure l; Figure l2 is a cross-sectional view taken along line XII-XII of Figure ll; Figure l3 is a cross-sectional view taken along line XIII-XIII of Figure ll; Figure l4 is a cross-sectional view taken along line XIV-XIV of Figure ll; and Figures l5 and l6 are views similar to Figures 3 and l0, respectively, but showing the structural components in a different mode of operation. Figure l shows a fastener-assembling apparatus embodying the present invention. The apparatus includes a generally C-shaped support or frame 20 vertically mounted on a table (not shown), the frame having a substantially L-shaped cross-section. The apparatus comprises a first parts feeder 2l supported on an upper end of the frame 20 for supplying first fastener elements A (Figure 2) in succession to a first chute 22, and a second parts feeder 23 suported on the frame 20 in tandem relation to the first parts feeder 2l for supplying second fastener elements B (Figure 2) in succession to a second chute 24. The apparatus further includes an upper or punch unit 25 disposed below the parts feeder 2l, a first drive mechanism 26 for vertically reciprocating a punch 27 of the upper unit 25, a first pusher mechanism 28 for receiving a first fastener element A from the first chute 2l and for supplying the first fastener element A to the upper unit 25, a lower or die unit 29 disposed below the upper unit 25, a second drive mechanism 30 for vertically reciprocating a die 3l of the lower unit 39, and a second pusher mechanism 32 for receiving a second fastener element B from the second chute 24 and for suplying the second fastener element B to the lower unit 25. The apparatus also comprises a third drive mechanism 33 for reciprocating an optical position indicator 34, a retainer mechanism 35 associated with the upper unit 25, a gate unit 36 associated with the upper unit 25 for opening and closing a feed passage 37 for the first fastener elements A, and a shock absorber 38 associated with the first drive mechanism 26. As shown in Figure 2, the first and second fastener elements A, B comprise a button body and a tack, respectively, of a button. The button body A includes a button back 39 which has an annular rim 40 covered by a cap 4l with a circular back plate 42 disposed between the button back 39 and the cap 4l. The cap 4l has a tongue 4l a underlying the rim 40. The button back 39 also has a hollow shank 43 in the from of a double tube projecting centrally from an inner edge of the annular rim 40. The tack B has a disc-like head 44 and a spike 45 projecting centrally from the head 44 for being forced through a garment fabric C (Figure l5) into the hollow shank 43 of the button back 39. The upper unit 25, as shown in Figure 3, includes a guide block 46 secured to the frame 20 and having a vertical guide channel 47 extending longitudinally therethrough, and a vertical slot 48 opening to the guide channel 47. The guide block 46 has a generally L-shape and includes a pair of spaced front and rear walls 49 (only one being shown) extending parallel to the frame 20, a side wall 50 joining the front and rear walls 49 along one edge thereof, and an elongate base 5l projecting perpendicularly from a lower end of the side wall 50. The guide channel 47 is defined by and between the walls 49, 50 and the slot 48 extends from the upper end to an intermediate portion of the side wall 50. The upper unit 25 further includes an elongate cover plate 52 secured to the front and rear walls 49 to close the guide channel 47 from a direction opposite to the side wall 50. The cover plate 52 has a vertical slot 53 extending longitudinally from a lower end to an intermediate portion of the cover plate 52. The upper unit 25 further includes a tubular holder 54 slidably received in the guide channel 47 in the guide block 46, the block 54 having a lower head portion 55 projecting outwardly downwardly from the guide channel 47. The holder 54 includes an abutment 56 projecting outwardly from an upper end thereof and received in the slot 53 in the cover plate 52. As shown in Figure 5, the holder 54 has a pair of clamp fingers 57, 57 slidably mounted in the head portion 55, and a pair of stop shoulders 58, 58 formed immediately above the head portion 55 and projecting laterally outwardly away from one another. The stop shoulders 58, 58 are engageable with lower ends 49 a , 49 a of the respective walls 49. The clamp fingers 57, 57 are urged toward each other by a pair of torsion springs 59 (only one shown in Figure 4) for holding a button body A below the punch 27 when the button body A is supplied from the first pusher mechanism 28 to clamp fingers 57, 57. When the punch 27 is lowered, the clamp fingers 57 are disposed away from each other against the force of the springs 59 to thereby release the button body A. The holder 54 further has a vertical hole 60 extending through the head portion 55 for the passage of the punch 27, and a concentric bore 6l of a large diameter extending contiguously upwardly from the hole 60. The clamp fingers 57 normally project in part into the hole 60. The punch 27 is detachably connected to the lower end of a cylindrical planger or ram rod 62 slidably received in the bore 6l in the holder 54, together with a split bush 63 fitted around the ram rod 62. The ram rod 62 is integral with the lower end of a ram 64 slidably received in the guide channel 47 in the guide block 46, the ram rod 62 having a length smaller than the length of the bore 6l. The split bush 63 has the same length of the ram rod 62 and is secured to the ram rod 62. The split bush 63 has a certain degree of radial resiliency so that it firctionally interconnects the holder 54 with the ram rod 62 for limited vertical movement therewith. The ram 64 is vertically reciprocated by the first drive mechanism 26 described below. While the ram 64 is at rest in an uppermost standby position, the ram 64 is vertically spaced from the holder 54 by a distance which is equal to the downward stroke of the punch 27. In this instance, the stopper shoulders 58 are held in contact with the lower ends 49 a of the front and rear walls 49 of the guide block 46. During the downward stroke of the ram 64 for clinching the button body A and the tack B, the holder 54 is lowered along with the punch 27 until it engages the lower unit 29. Then the ram 64 further moves downwardly until it engages an upper end of the holder 54 during which time the punch 27 is lowered along the hole 60. When the ram 64 arrives at its lowermost position, the lower end face of the punch 27 lies flush with the lower end face of the holder 54. The retainer mechanism 35, as shown in Figure 3, is incorporated in the ram 64 and includes an elongate hook 65 and a compression coil spring 66. The hook 65 is movably received in the slot 53 in the cover plate 52 and is pivotably connected to the ram 64 by a pin 67 extending horizontally across a recess 68 in the ram 64 in which a central lateral projection 69 of the hook 65 is loosely received. The hook 65 has at its lower end a locking projection 70 lockingly engageable with the abutment 56 on the holder 54 to hold an element-receiving space between the clamp fingers 57 in horizontal alignment with the element-feed passage 37 while the ram 64 is at rest in the uppermost standby position. The compression coil spring 66 is received in a blind hole 7l in the ram 64 and acts between the ram 64 and the upper end of the hook 65 to urge the hook 65 to turn counterclockwise in Figure 3. The first drive mechanism 26 includes a fluid-pressure actuator such as an air cylinder 72 and a toggle joint 73 composed of a pair of first and second levers 74, 75. The first lever 74 is pivotably connected at its one end to the guide block 46 by a horizontal shaft 76 extending between the front and rear walls 49 of the guide block 46, the other end of the first lever 74 being pivotably connected to a piston rod 77 of the air cylinder 72. The second lever 75 is pivotably connected at opposite ends to the first lever 74 and the upper end of the ram 64. For connection, the levers 74, 75 extend into the vertical bore 47 through the vertical slot 48 in the guide block 46. The air cylinder 72 includes a cylinder tube 78 pivotably connected to one end of a pivot lever 79 rotatably supported on the frame 20 by a horizontal shaft 80, so that the air cylinder 72 is pivotably supported by and between the toggle joint 73 and the pivot lever 79. In response to reciprocating movement of the piston rod 77, the first and second levers 74, 75 are pivotably moved relative to each other between a contracted position in which the two levers 74, 75 are disposed substantially at a right angle to one another (Figure 3), and an extended position in which the two levers 74, 75 are disposed substantially in a vertical straight line (Figure l5). Thus, as the two levers 74, 75 are moved between the contracted and extended positions, the ram 64 and hence the punch 27 is moved vertically between the uppermost standby position and a lowermost clinching position. The first pusher mechanism 28 includes a cushioning rod 8l pivotably connected at its one end to the other end of the pivot lever 79, an actuating lever 82 pivotably supported on the frame 20 by a shaft 83, a tubular connecting bar 84 operatively interconnecting the cushioning rod 8l and one end of the actuating lever 82, and an upper pusher 85 pivotably connected at its rear end to the other end of the actuating lever 82 and slidably supported by the guide block 46. The cushioning rod 8l has a presser member 86 in the form of an annular disc fixedly connected to the rod 8l at an intermediate portion thereof. The presser member 86 may be integrally with the cushioning rod 8l. A portion of the cushioning rod 8l extending between the free end of the rod 8l and the presser member 86 is received in the tubular connecting bar 84 and slidably supported by an annular end bush 87 fitted to one end of the connecting bar 84. A compression coil spring 88 is disposed around the cushioning rod 8l and acts between the end bush 87 and a stop ring 89 secured to the free end of the rod 8l so as to urge the cushioning rod 8l leftwardly in Figure 3 until the presser member 86 engages the end bush 87. The other end of the tubular connecting bar 84 is closed by an end cap 90 to which the actuating lever 82 is pivoted. The upper pusher 85 is urged upwardly by a tension coil spring 9l acting between the upper pusher 85 and a horizontal pin 92 secured to the frame 20. In response to retracting movement (rightward direction in Figure 3) of the cylinder tube 78, the pivot lever 79 is turned clockwise about the shaft 80 to cause the pressure member 86 to positively move the connecting bar 84 leftwardly. Thus, the actuating lever 82 is turned counterclockwise about the shaft 83 to thereby retract the upper pusher 85 away from the clamp fingers 57. Conversely, the upper pusher 85 is advanced in response to angular movement of the pivot lever 79 in the counterclockwise direction which is caused by the forward movement (leftward direction in Figure 3) of the cylinder tube 78. The reaward movement of the cylinder tube 78 is limited by a slide rod 93 slidably supported on a block 94 secured to the frame 20. One end of the slide rod 93 is pivotably connected to one end of the pivot lever 79 adjacent to the cylinder tube 78, and the other end of the slide rod 93 is externally threaded and projects from the block 94, as shown in Figure 3. The slide rod 93 has an enlarged annular flange 95 disposed between the pivot lever 79 and the block 94, the flange 95 being engageable with the block 94 to limit rearward movement of the cylinder tube 78. An annular spring retainer 96 is threaded to the other end of the slide rod 93. A compression coil spring 97 is disposed around the spring retainer 96 and acting between the block 94 and the retainer 96 to urge the slide rod 93 rightwardly. The spring 97 biases the slide rod 93 and hence the air cylinder 72 such that during a portion of the movement of the piston rod 77 from the cylinder tube 78 adjacent the fully retracted position of the piston rod 77, the pivot lever 79 operates the linked components 8l, 82, 84 to retract and advance the upper pusher 85. In response to reciprocating movement of the piston rod 77, the flange 95 and the retainer 96 alternately engage the block 94. Thus the pivot lever 79 and the spring-biased slide rod 93 jointly constitute a combined supporting and connecting mechanism for slidably and pivotably supporting the air cylinder 72 on the frame 20 and also for operatively connecting the air cylinder 72 and the first pusher mechanism 20. The shock absorber 38 is disposed adjacent to the spring retainer 96 and includes a dashpot 98 supported on a bracket 99, and an annular cushion ring l00 attached to one end face of the spring retainer 96 in confronting relation to the bracket 99. The dashpot 98 has a piston rod l0l extending through the bracket 99 in alignment with the slide rod 93. The piston rod l0l is normally held in an extended position, such as shown in Figure 3 and, upon engagement with the slide rod 93, it is retractable to dampen and control a motion of the slide rod 93 in such a manner that the flange 95 can be brought into contact with the block 94 without generating shock noises and vibration. The cushion ring l00 is made of a resiliently deformable material such as synthetic resin or rubber foam and is engageable with the bracket 99 slightly before the engagement of the flange 95 with the block 94. As shown in Figures 6 through 9, inclusive, a lower portion of the first chute 22, the third drive mechanism 33 and the gate unit 36 are disposed adjacent to the base 5l of the guide block 46. The lower portion of the chute 22 extends from the rear side of the frame 20 to a position beneath the base 5l (Figure 7) and has a discharge end disposed in registry with the element-receiving space between the clamp fingers 57 when the holder 54 is held in the position of Figure 5. The chute 22, as shown in Figure 7, includes a chute body l02 having a longitudinal guide groove l03 defined therein for the passage of the button body A, and a pair of L-shaped cover plates l04 attached to the body l02 to partly close a lower open side of the guide groove l03 for preventing displacement of the button body A from the chute body l02. The chute body l02 is secured to the base 5l of the guide block 46. The button body A, as it slides down along the guide groove l03, takes the posture of Figure 2, in which the hollow shank 43 is facing downwardly. The discharge end of the chute 22 has a retaining groove l05 extending transversely to the guide groove l03 for temporarily holding therein the button body A. The retaining groove l05 constitutes with a portion of the element-feed passage 37. The gate unit 36 includes a rectangular guide plate l06 having substantially the same length as the base 5l, and a rectangular slide block l07 having a length smaller than the length of the base 5l. The guide block l06 is secured to a front wall of the base 5l remote from the frame 20 (Figure 7) and includes a horizontal guide ridge l08 extending along a lower longitudinal edge of the guide block l06 in parallel spaced relation to a lower wall of the base 5l. The slide block l07 has a generally L-shape and is disposed below the base 5l in confronting relation to the discharge end of the chute 22. The slide block l07 has, throughout the length thereof, a horizontal guide recess l09 slidably fitted with the guide ridge l08 on the guide block l06, and a lateral projection ll0 slidably fitted with a guide step lll formed in the chute body l02. Thus, the slide block l07 is slidable in a direction parallel to the feed passage 37. As shown in Figures 6 and 8, the slide block l07 has a pair of parallel spaced vertical grooves ll2 extending transversely to the guide recess l09. The grooves ll2 receive therein a pair of spring-loaded balls ll3, respectively, movably retained on a tubular holders ll4 threaded to the guide plate l06. The spring-biased balls ll3 and the grooves ll2 jointly constitute a detent assembly for positioning the slide block l07 with respect to the guide plate l06 and the chute 22. As shown in Figure 7, the gate unit 36 also includes a retainer finger ll5 slidably received in a horizontal slot ll6 extending transversely through the slide block l07 in alignment with the discharge end of the chute 22. The retainer finger ll5 has a retaining recess ll7 defined in an inner end face thereof and a stop lug ll8 projecting laterally from the outer end of the retainer finger ll5. The retaining recess ll7 is complementary in contour to the guide groove l03 in the chute 22. The retainer finger ll5 is normally urged toward the chute 22 by means of a leaf spring ll9 until the stop lug ll8 engages the slide block l07. Under such condition, one button body A is stably receivable in the retaining recess ll7 in the retainer finger ll5 and the retaining groove l05 in the chute 22. Although not shown, the inner end of the retainer finger ll5 has a bevelled cam surface engageable with a front end of the upper pusher 85 to retract the retainer finger ll5 against the force of the leaf spring ll9 when the upper pusher 8l is advanced. The slide block l07, throughout the length thereof, has a horizontal groove l20 (Figure 8) opening toward the retaining groove l05 in the chute 22 and communicating at one end with the retaining recess ll7 in the retainer finger ll6, the groove l20 constituting a part of the element-feed passage 37. The slide block l07 further has a horizontal guide channel l2l extending longitudinally for the passage of the upper pusher 85, the guide channel l2l opening downwardly. To move the slide block l07 relative to the guide plate l06, a knob l22 is attached to the slide block l07. The third drive mechanism 33, as shown in Figure 6, includes a slide bar l23, a tension coil spring l24, a retainer block l25, a follower member l26, and a support lever l27. The slide bar l23 is slidably received in a horizontal guide groove l28 extending longitudinally in the base 5l and has one end projecting from the guide groove l28. The tension coil spring l24 extends between a first retainer pin l29 secured to the guide plate l06 and a second retainer pin l30 secured to the exposed end of the slide bar l23, and urges the slide bar l23 toward the punch 27 (Figure 3). The retainer block l25 is of a generally channel shape having a pair of parallel spaced legs l3l, l32, one of which is fastened to the exposed end of the slide bar l23. The second retainer pin l30 extends through the slide bar l23 and through the legs l3l, l32 across a space defined between the legs l3l, l32. The follower member l26 comprising a roller of synthetic rubber is rotatably mounted on a portion of the retainer pin l30 extending between the legs l3l, l32. The roller follower l26 is disposed in confronting relation to the actuating lever 82 with a space leaving therebetween. The leg l3l of the retainer block l25 has an upper extension normally held in contact with a stopper bolt l33 threaded to the base 5l. The stopper bolt l33 is axially movable to adjust the distance between the actuating lever 82 and the roller follower l26. The support lever l27 has an L-shape and is connected at its one end to the slide bar l23 at a position between the base 5l and the retainer block l25. The support lever l27 has a support arm l34 extending from the other end of the lever l27 toward the frame 20. The optical position indicator 34 is mounted on the support arm l34 in such a manner that it can issues a light beam extending in alignment with the path of movement of the punch 27 when the slide lever l23 is in the position of Figure 6. As shown in Figures l0 and l3, the lower unit 29 includes an elongate guide base l35 fixedly supported by the frame 20. The guide base l35 has a T-shaped longitudinal guide rib l36 extending on an upper surface thereof for retaining a pair of parallel guide plates l37, l37. Each of the guide plates l37 has a horizontal projection l38 extgending along an upper longitudinal edge thereof and projecting toward the projection l38 on the opposite guide plate l37. The two projections l38 are spaced from one another by a slot l39 in and along which a lower pusher l40 of the second pusher mechanism 32 is movable, the slot l39 opening to a hollow space l4l defined between the guide plates l37. Connected to one end (left end in Figure l0) of the guide base l35 is a guide block l42 having a vertical guide channel l43 extending longitudinally therethrough, and a vertical slot l44 opening to the guide channel l43 for the passage of the lower pusher l40. The guide block l42 includes a pair of spaced front and rear walls l45 (only one shown) extending parallel to the frame 20, and a side wall l46 joining the front and rear walls l45 along one longitudinal edge thereof. The side wall 46 includes a lower portion secured to the guide base l35, and an upper portion in which the vertical slot l44 is formed. The guide channel l43 is defined jointly by and between the walls l45, l46. The lower unit 29 further includes a cover plate l47 secured to the front and rear walls l45 to close the guide channel l43 from a direction opposite to the side wall l46. The cover plate l47 has a vertical recess l48 opening to the guide channel l43. As shown in Figure l2, the front and rear walls l45 have a pair of aligned oblong holes l49, l49, respectively, extending along upper portions of the respective walls l45 and communicating with the guide channel l43. The lower unit 29 further includes a tubular holder l50 slidably fitted over the die 3l. The holder l50 is slidably received in the guide channel l43 and vertically movable with respect to the guide block l42 for a limited distance which is determined by the stroke of a lateral projection l5l (Figure l0) on the holder l50 slidably received in the vertical recess l48 in the cover plate l47. The holder l50 has a pair of inverted L-shaped recesses l52, l52 defined in its outer peripheral surface in registry with the oblong holes l49, l49, each recess l52 having an upper end opening to a vertical hole l53 in the holder l50. A pair of inverted L-shaped clamp fingers l54, l54 is received in the respective recesses l52 and they are pivoted at their lower ends to the holder l50 by means of a pair of pins l55, l55. The clamp fingers l54 are urged toward each other by a pair of leaf springs l56, l56 for holding a tack B above the die 3l when the tack B is supplied from the lower pusher l40 to the holder l50. The leaf springs l56 are secured at their lower ends to the respective walls l45 of the guide block l42, the other ends of the springs l56 acting on the clamp fingers l54. The clamp fingers l54 have a pair of bevelled lower surfaces l57, respectively, sloping upwardly convergently toward each other. When the die 3l is moved upwardly toward its uppermost clinching position, the lower surfaces l57 are engageable with the die 5l to pivot the clamp fingers l54 about the pins l55 outwardly away from one aother against the force of the leaf springs l56. When the die 3l arrives at the uppermost clinching position, the upper surface of the die 3l lies flush with the upper surface of the holder l50. The holder l50 further has a vertical bore l58 extending concentrically with and downwardly from the vertical hole l53 for receiving a cylindrical plunger rod l59 to which the die 3l is connected. The bore l58 has a diameter larger than the diameter of the hole l53. The plunger rod l59 is integrally formed with the upper end of a plunger l60 slidably received in a plunger holder l6l secured to the guide block l42. There is a compression coil spring l62 disposed around the plunger rod l59 and acting between the plunger holder l6l and the holder l50 to urge the latter upwardly. As shown in Figure l0, the second drive mechanism 30 includes an actuating lever l63, a fluid-pressure actuator such as an air cylinder l64, and a connecting rod l65 operatively interconnecting the actuating lever l63 and the air cylinder l64. The actuating lever l63 is pivotably mounted on the frame 20 by a horizontal shaft l66 secured to the frame 20, and has one end pivotably connected to a lower end of the plunger l60. The other end of the actuating lever l63 is pivotably connected to one end of the connecting rod l65 by a short link lever l67. The other end of the connecting rod l65 is fixedly secured to a piston rod l68 of the air cylinder l64. The air cylinder l64 is fixedly supported on the frame 20 in a vertical disposition. With this construction, when the air cylinder l64 is actuated to extend its piston rod l68, the actuating lever l63 is turned clockwise about the shaft l66 to move the plunger l60 and hence the die 3l toward its uppermost clinching position (Figure l6). Conversely, retracting movement of the piston rod l68 causes the actuating lever l63 to turn counterclockwise about the shaft l66, thereby lowering the die 3l toward its lowermost standby position (Figure l0). The second pusher mechanism 32, as shown in Figure l0, includes a cam block l69 secured to the connecting rod l65, a cam follower l70 engaging the cam block l69, a pivot lever l7l supporting the cam follower l70, a spring loaded actuating lever l72 linked with the pivot lever l7l by means of a link lever l73, and the lower pusher l40 connected to the actuating lever l72. The cam block l69 has a lower sloping cam surface l74 engageable with the cam follower l70 to cause the pivot lever l7l to turn clockwise, and an upper flat cam surface l75 extending contiguously upwardly from the sloping cam surface l74 and engageable with the cam follower l70 to hold the pivot lever l7l non-rotatably in a tilted position. The cam follower l70 comprises a roller of a resilient material such as rubber and is rotatably mounted on a lower end of the pivot lever l7l, the roller follower l70 being normally held in contact with the sloping cam surface l75. The pivot lever l7l is pivoted to the frame 20 by means of a horizontal shaft l76 and is pivotably connected at its upper end to one end of the link lever l73. The opposite end of the link lever l73 is pivotably connected to an intermediate portion of the actuating lever l72. The actuating lever l72 is pivoted at its upper end to the frame 20 by means of a horizontal shaft l77 and has a lower end pivotably connected to a rear end of the lower pusher l40. The actuating lever l72 is urged to turn clockwise about the shaft l77 by means of a tension coil spring l78 extending between a retainer pin l79 secured to the frame 20 and a retainer pin l80 secured to the actuating lever l72. The lower pusher l40 is slidably received in the slit l39 (Figure l3) and is urged upwardly by a tension coil spring l8l extending between the lower pusher l40 and a retainer pin l82 secured to the actuating lever l72. To hold the lower pusher l40 in horizontal posture, a pair of cover plates l83, l83 (Figures ll and l3) is secured to the respective guide plates l37 to conceal the lower pusher l40. The cover plates l83 jointly define therebetween an interior guide groove l84 opening to the slit l39 for receiving an upper longidudinal portion of the lower pusher l40. With the second pusher mechanism 32 thus constructed, when the air cylinder l64 is energized to extend its piston rod l68, the roller follower l70 rolls on and along the sloping cam surface l74 on the cam block l69 to thereby turn the pivot lever l7l clockwise (Figure l0) about the shaft l76. This angular movement of the pivot lever l70 causes the actuating lever l72 to turn counterclockwise about the shaft l77 against the force of the tension spring l78, whereupon the lower pusher l40 is held in its fully retracted position. In response to contraction of the piston rod l68, the roller follower l70 moves from the flat cam surface l75 to the sloping cam surface l74, causing the pivot lever l72 to turn counterclockwise about the shaft l76. This angular movement of the pivot lever l7l causes the actuating lever l72 to turn clockwise about the shaft l77 under the force of the tension spring l78 whereupon the lower pusher l40 is advanced toward the holder l50. The stroke of the lower pusher l40 depends on the length of the sloping cam surface l74 and is independent from the stroke of the piston rod l68. This arrangement is advantageous in applications wherein the garment fabrics C vary in thickness. The stroke of the lower pusher l40 is always constant and any change in thickness of the garment fabrics C is accomodated by the provision of the flat cam surface l75. The lower pusher l40 has on its upper surface a first presser ridge l85 provided at the forward end, a second presser ridge l86 spaced rearwardly from the first presser ridge l85 by a distance equal to the stroke of the lower pusher l40, and a third presser ridge l87 spaced rearwardly from the second presser ridge l86 by the distance or stroke of the pusher l40. Each of the first to third presser ridges l85 - l86 has a sloping cam surface l85 a , l86 a , l87 a facing rearwardly toward the actuating lever l72. As shown in Figure l3, the cover plates l83, l83 have a pair of confronting recessed lower longitudinal edges l88, l88 contiguous to the guide groove l84, the recess l88 and the guide groove l84 jointly defining an elongate feed passage l89 for the tacks B. As seen from Figure l6, the second chute 24 has a discharge end located adjacent to the third presser ridge l87 when the lower pusher l40 is fully retracted. Stated in other words, the discharge end of the second chute 24 is spaced rearwardly from the third presser ridge l87 by a distance equal to the stroke of the lower pusher 40 when the latter is fully advanced. The second chute 24, as shown in Figure l3, includes a lower portion extending from the rear side to the front side of the frame 20 and disposed on the guide plate l37 located near the frame 20. The cover plate l83 disposed on this guide plate l37 is shorter than the other cover plate l83 and has a rear end held in contact with an outer edge of the chute 24 (Figure l0). The second chute 24 includes a chute body l90 having a longitudinal guide groove l9l defined therein for the passage of the tacks B, and a pair of L-shaped cover plates l92 (only one shown) attached to the chute body l90 to partly close an upper open side of the guide groove l9l for prevent detachment of the tack B from the chute body l90. The chute body l90 is connected to the guide plate l37 through a bracket l93 fastened to the chute body l90 and the guide plate l37. The tack B, as it slides down along the guide groove l9l, takes the posture shown in Figure 2, in which the spike 45 is directed upwardly. The discharge end of the chute 24 has a retaining groove l94 extending transversely to the guide groove l9l for temporarily holding therein the tack B. The retaining groove l94 communicates with the feed passage l89 (Figure l3). As shown in Figure l0, the chute body l90 further has a bevelled cam surface l95 engageable with the sloping cam surface l87 a on the third presser ridge l87 to urge the lower pusher l40 to tilt downwardly into the space l4l (Figure l3). As shown in Figures ll and l4, a retainer finger l96 is slidably supported on the guide plate l37 in confronting relation to the discharge end of the chute 24. The retainer finger l96 has a retaining recess l97 defined in an inner end face thereof and a stop lug l98 projecting upwardly from the rear end of the retainer finger l96. The retaining recess l97 is complementary in contour to the guide groove l9l in the chute 24. The retainer finger l96 is normally urged toward the chute l4 by means of a leaf spring l99 until the stop lug l89 abuts against the guide plate l37. Under such condition, one tack B is stably receivble in the retaining recess l97 in the retainer finger l96 and in the retaining groove l94 in the chute body l90. Although not shown, the retainer finger l96 has a bevelled cam surface engageable with the third presser ridge l87 of the lower pusher l40 to retract the retainer finger l96 against the bias of the leaf spring l99 when the lower pusher l40 is advanced. A pair of parallel spaced retainer plates 200 is fixedly disposed between the guide plates l37 to prevent lateral displacement of the lower pusher l40 while the latter is in motion. As shown in Figures l0 and ll, a pair of first and second retainer arms 20l, 202 is slidably mounted in the guide plate l37 disposed close to the frame 20. The first retainer arm 20l is disposed at a position spaced forwardly from the disharge end of the chute 24 by a distance equal to the stroke of the lower pusher l40. Likewise the second retainer arm 202 is spaced forwardly from the first retainer arm 20l by the same distance as the stroke of the lower pusher l40. Each of the retainer arms 20l, 202 has a stepped front end 203 and is urged by a torsion spring 204 toward an advanced position in which the stepped front end 203 is party projecting into the slit l39 for temporarily holding one tack B. The first retainer arm 20l has a first cam surface 20l a (Figure ll) engageable with the second presser ridge l86 to retract the first retainer arm 20l when the lower pusher l40 is advanced, and a second cam surface 20l b (Figure l0) engageable with the cam surface l86 a on the second presser ridge l86 to tilt the lower pusher l40 downwardly into the space l4l between the guide plates l37 as the lower pusher l40 is retracted. Likewise, the second retainer arm 202 has a first cam surface 202a (Figure ll) engageable with the first presser ridge l85 to retract the second retainer arm 202 when the lower pusher l40 is advanced, and a second cam surface 202 b (Figure l0) engageable with the cam surface l85 a on the first presser ridge l85 to tilt to lower pusher l40 downwardly into the space l4l as the lower pusher l40 is retracted. With this construction, when the actuating lever l72 is turned counterclockwise in Figure l0 to retract the lower pusher l40, the cam surfaces l85 a -l87 a on the first to third presser ridges l85 - l87 are brought into engagement respectively with the second cam surfaces 202 b , 20l a of the retainer arms 202, 20l and the cam surface l95 of the chute 24. This engagement causes the lower pusher l40 to tilt downwardly into the space l4l against the bias of the tension spring l8l so that the respective presser ridges l85 - l87 can be located rearwardly of the three tacks B held respectively on the stepped front ends 203 of the retainer arms 202, 20l and in a position adjacent to the discharge end of the chute 24. In response to clockwise angular movement of the actuating lever l72, the lower pusher l40 is advanced along a horizontal path, during which time the three tacks B are fed by the first to third presser ridges l85 - l87 respectively to the holder l50, the second retainer arm 202 and the first retainer arm 20l. The fastener-assembling apparatus of the foregoing construction operates as follows: For perposes of illustration, operation of the apparatus begins from a condition shown in Figures l, 3, 6 and l0 where the piston rods 77, l68 of the air cylinders 72, l64 are fully retracted. Thus, the punch 27 and the die 3l are fully retracted, while the upper and lower pushers 85, l40 are fully advanced so that a button body A is held by the clamp fingers 57 below the punch 27 and a tack B is held on the die 3l by the clamp fingers l54. The position indicator 34 assumes its advanced position and the light beam projected therefrom passes along the common vertical axis of the button body A and the tack B. The light beam produces a light spot on a garment fabric C (Figure l5) when the latter is disposed between the upper and lower units 25, 29. After a position on the garment fabric C where the button body A and the tack B are to be attached has been set in registry with the light sopt, the air cylinders 72, l64 are actuated to extend their piston rods 77, l68. In immediate response to actuation of the air cylinder 72, and more particularly while the piston rod 77 undertakes a portion of its advancing movement from the cylinder tube 78 adjacent to the fully retracted position, the slide rod 73 and hence the cylinder tube 78 are moved rightwardly in Figure 3 under the force of the spring 97, thereby causing the pivot lever 79 to turn clockwise about the shaft 80 until the flange 95 on the slide rod 93 engages the block 94. During that time, the shock absorber 38, the first pusher mechanism 28, and the third drive mechanism 33 are put in action. In response to the forward movement of the piston rod 77, the spring retainer 96 of the shock absorber 38 moves rightwardly away from the block 94 under the force of the spring 97 to cause the slide rod 93 to first engage the piston rod l0l of the dashpot 98 and then to force the piston rod l0l to retract into the dashpot 98. The dashpot 98 controls the motion of the slide rod 93 in such a manner that the flange 95 on the slide rod 93 can be brought into gentle contact with the block 94 without generating objectionable shock noise and vibration. Slightly before the engagement of the flange 95 with the block 94, the cushioning ring l0 engages the bracket 99 to absorb the shock noise and vibration when the spring retainer 96 is brought into engagement with the bracket 99 under the force of the spring 97. When the pivot lever 79 is turned clockwise about the shaft 80, the presser member 86 of the cushioning rod 8l positively moves the connecting bar 84 leftwardly to thereby turn the actuating lever 82 counterclockwise about the shaft 83. Thus, the upper pusher 85 is retracted from the position of Figure 3 to the position of Figure l5 in preparation for feeding of the next suceeding button body A. Subsequent to the begining of the rearward movement of the upper pusher 85, the actuating lever 82 engages the roller follower l26 (Figure 6) and then urges the slide bar l23 to retract against the bias of the spring l24. Consequently, the optical position indicator 34 is retracted away from the path of movement of the punch 27. Due to the space provided initially between the actuating lever 82 and the roller follower l26, there is provided a time lag between the movement of upper pusher 85 and the movement of the position indicator 34 with the result that an additional period of time is available for monitoring the position setting of the garment fabric 3 with respect to the path of movement of the punch 27. Furthermore, the position indicator 34 is driven independently from the upper pusher 85 and has a stroke shorter than that of the upper pusher 34. This arrangement is therefore relatively compact and enables a reliable positioning of the garment fabric C without interference with the position indicator 34. As the piston rod 77 of the air cylinder 72 further advances after the engagement of the flange 95 with the block 94, the toggle joint 73 extends its levers 74, 75 to thereby lower the ram 64 and hence the punch 27. As the holder 54 is frictionally coupled with the ram rod 62 by the split bush 63, the holder 54 is lowered together with the punch 27 until it is brought into abutment with the garment fabric C which is placed over the holder l50 of the lower unit 29. Continuing downward movement of the ram 64 causes the punch 27 to move downwardly through the vertical hole 60 (Figure 5) in the holder 54 to force the button body A into clinching engagement with the tack B which is forced to drive through the garment fabric C into the button body A as the die 3l is moved upwardly in synchronism with the downward movement of the punch 27. The operation of the lower half of the apparatus will be described later on. When the punch 27 is fully descended as shown in Figure l5, the locking projection 70 on the retainer hook 65 is vertically downwardly spaced from the abutment 56 of the upper unit 25. Upon completion of the clinching operation of the button body A and the tack B, the air cylinder 72 is actuated to retract its piston rod 77, whereupon the toggle joint 73 contracts its levers 74, 75 to move the ram 64 and hence the punch 27 upwardly. Due to the resilient force of the split bush 63 acting between the holder 54 and the ram rod 62, the holder 54 moves upwardly along with the punch 27 until the stop shoulders 58 of the holder 54 abut against the lower ends 49 a of the guide block 46, as shown in Figure 5. In this instance, the abutment 56 on the holder 54 is hooked on the locking projection 70 of the retainer hook 65 so that the holder 54 is retained in the uppermost element-receiving position in which 54 the space between the clamp fingers 57 is held in alignment with the feed passage 37. With the retainer 34 thus provided, the button body A can be held stably and reliably by the clamp fingers 57. Contraction of the toggle joint 73 and hence the upward movement of the punch 27 is limited when the lever 74 engages the stopper member 204. Thereafter, the piston rod 77 of the cylinder 72 is retractable to such an extent that the cylinder tube 78 is pulled toward the toggle joint 73 to turn the pivot lever 79 counterclockwise about the shaft 79 against the force of the spring 79. This angular movement of the pivot lever 79 is terminated when the spring retainer 96 is brought into engagement with the block 94. In response to the counterclockwise angular movement of the pivot lever 79, the connecting bar 84 is pulled rightwardly while the presser member 86 is held in contact with the connecting bar 84 under the force of the spring 88. Consequently, the actuating lever 82 is turned clockwise about the shaft 82 to move the upper pusher 85 forwardly along the feed passage 37 for supplying the next button body A to the holder 54. In this instance, when the forward movement of the upper pusher 85 is interupted by a foreign matter jamming the feed passage 37, angular movement of the pivot lever 79 will move the cushioning bar 8l righwardly against the bias of the spring 88 while the connecting bar 84 remains immoval. With this arrangement, the button bodies A can alway be protected against damage or deformation even in the presence of a foreign matter in the feed passage 37. In response to the clockwise angular movement of the actuating lever 82, the slide bar l23 is advanced under the force of the spring l24 until the leg l3l of the retainer block l25 engages the stop bolt l33, thereby displacing the position indicator 34 to the advanced indicating position. When a foreign matter or a button body A is jamming the feed passage 37, the slide block l07 of the gate unit 36 is slid along the guide ridge l08 on the guide plate l06 until the discharge end of the first chute 22 is exposed or at least until the jamming material in the feed passage 37 is exposed. Thus, the jamming material can easily be removed by the operator. The operation of the lower half of the apparatus is described below with reference to Figures l0 and l6. When the air cylinder l64 is actuated to extend its piston rod l68, the connecting rod l65 and hence the cam block l69 is lowered. Relatively to the downward movement of the cam block l69, the roller follower l70 rolls along the sloping cam surface l74 to turn the pivot lever l7l clockwise about the shaft l76. This angular movement of the pivot lever l7l causes the actuating lever l72 to turn counterclockwise about the shaft l77 against the bias of the spring l78. Consequently, the lower pusher l40 is retracted away from the holder l50. A continuing forward movement of the piston rod l68 causes the roller follower l70 to move from the sloping cam surface l74 to the flat cam surface l75 whereupon the movement of the pivot and actuating levers l7l, l72 come to a halt in the respective tilted positions. Accordingly, the lower pusher l40 is posing in the retracted standby position in which the first to third presser ridges l85 - l87 are located in the feed passage l89 (Figure l3), immediately upstream of the next succeeding three tacks B respectively retained on the second retainer arm 202, the first retainer arm 20l and the discharge end of the second chute 24. The forward movement of the piston rod l68 also causes the actuating lever l63 to turn the actuating lever l63 clockwise about the shaft l66 whereupon the plunger l60 and the die l30 are moved upwardly in unison. The povot point on the actuating lever l63 is located closer to the plunger l60 than to the piston rod l68 so that the die 3l does not interface with the lower pusher l40 while they are in motion. While the upper pusher l40 is kept immovable in the standby position, the die 3l is moved upwardly along the hole l53 (Figure l2) in the holder l50 to thereby clinch the tack B and the button body A with the garment fabric C sandwiched therebetween. Thereafter, the air cylinder l64 is actuated to retract its piston rod l68 whereupon the cam block l69 is moved upwardly from the position of Figure l6 to the position of Figure l0. During that time, the lower pusher l40 remains immovable until the roller follower l70 moves from the flat cam surface l75 to the sloping cam surface l75, whereupon the pivot lever l7l turns counterclockwise about the shaft l75. This angular movement of the pivot lever l7l permits the actuating lever l72 to turn clockwise about the shaft l77 under the force of the spring l78. Consequently, the lower pusher l40 is advanced horizontally toward the holder l50 to feed the next suceeding three tacks B, respectively, onto the die 3l, the second retainer arm 202 and the first retainer arms 20l. Retracting movement of the piston rod l68 also causes the actuating lever l63 to turn counter-clockwise about the shaft l66 to thereby lower the plunger l60 and hence the die 3l to the standby position. As the stroke of the die 3l and the stroke of the lower pusher l40 are independent from one another, a stable clinching operation is reserved even when the button bodies A and the tacks B are to be attached to garment fabrics C of different thicknesses.

Claims: An apparatus for assembling a pair of fastener elements (A, B) of a garment fastener with a garment fabric (C) disposed between the two fastener elements (A, B), comprising: (a) a frame (20); (b) a pair of vertically aligned upper and lower units (25, 29) supported by said frame (20) for receiving the respective fastener elements (A, B), said upper unit (25) having a punch (27), said lower unit (29) having a die (3l), said punch (27) and said die (3l) being reciporcably movable toward and away from each other to join the two fastener elements (A, B) together with the garment fabric (C) sandwiched therebetween; (c) a first drive mechanism (26) for reciprocating said punch (27), said first drive mechanism (26) including a fluid-pressure actuator (72) having a piston rod (77) and a cylinder tube (78); (d) a first pusher mechanism (28) including first means supported by said frame (20) and defining a first feed passage (37) receptive of one fastener element (A), said first pusher mechanism (28) also including a first pusher (85) reciprocable within said first feed passage (37) to push the one fastener element (A) therethrough to said upper unit (25); (e) a second drive mechanism (30) for reciprocating said die (3l); and (f) a second pusher mechanism (32) including second means supported by said frame (20) and defining a second feed passage (l89) receptive of the other fastener element (B), said second pusher mechanism (32) also including a second pusher (l40) reciprocable within said second feed passage (l89) to push the other fastener element (B) therethrough to said lower unit (29); characterized by (g) a combined supporting and connecting mechanism (79, 93) for slidably and pivotably supporting said fluid-pressure actuator (72) on said frame (20) and also for operatively connecting said fluid-pressure actuator (72) and said first pusher mechanism (28), said combined mechanism (79, 93) including a pivot lever (79) rotatably mounted on said frame (20) and pivotably connected at opposite ends with said cylinder tube (78) and said first pusher mechanism (28), and a spring-biased slide rod (93) slidably mounted on said frame (20) and pivotably connected at its one end to said pivot lever (79) adjacent to said cylinder tube (78), said slide rod (93) being normally urged in a direction such that during a portion of the movement of said piston rod (77) from said cylinder tube (78) adjacent the fully retracted position of said piston rod (77), said pivot lever (79) operates said first pusher mechanism (28) to retract and advance said first pusher (85). An apparatus according to claim l, said first pusher mechanism (28) further including a cushioning rod (8l) pivoted at its one end to the other end of said pivot lever (79), an actuating lever (82) pivotably supported on said frame (20) and pivoted at its one end to a rear end of said first pusher (85), a tubular connecting bar (84) pivotably connected at one of its opposite ends to the other end of said actuating lever (82) and loosely receiving said cushioning rod (8l) from the other end thereof, a presser member (86) disposed on said cushioning rod (8l) and engageable with the other end of said connecting bar (84), and biasing means (88) disposed in said tubular connecting bar (84) and acting between said connecting bar (84) and said cushioning rod (8l) for urging the latter in a direction to keep said presser member (86) in engagement with said other end of said connecting rod (84). An apparatus according to claim 2, said biasing means comprising a compression coil spring (88) disposed around a longitudinal portion of said cushioning rod (8l) which is received in said tubular connecting rod (8l). An apparatus according to claim l, said spring-biased slide rod (93) including a flange (95) engageable with said frame (20) to limit movement of said slide rod (93) in said direction, further including a shock absorber (38) cooperative with said slide rod (93) to absorb shock noise and vibration when said flange (95) engages said frame (20). An apparatus according to claim 4, said shock absorber (38) including a dashpot (98) mounted on said frame (20) adjacent to the other end of said slide rod (93) and having a piston rod (l0l) engageable with said other end of said slide rod (93) prior to the engagement of said flange (95) with said frame (20). An apparatus according to claim 5, said spring-biased slide rod (93) including an annular spring retainer (96) secured to said other end of said slide rod (93) and having one end engageable with said frame (20) to limit movement of said slide rod (93) in a direction opposite to the first-mentioned direction, and a compression coil spring (97) disposed around said spring retainer (96) and acting between said frame (20) and said spring retainer (96) to urge the latter in said first-mentioned direction, said dashpot (98) being supported on a bracket (99) secured to said frame (20) in confronting relation to the other end of said annular spring retainer (96), said shock absorber (38) further including a resiliently deformable cushioning ring (l00) disposed on said other end of said spring retainer (96) and engageable with said bracket (99) prior to the engagement of said flange (95) with said frame (20). An apparatus according to claim l, said first drive mechanism (26) including a reciprocable ram (64) driven by said fluid-pressure actuator (72) and having a ram rod (62) connected to said punch (27), said upper unit (25) including a tubular holder (54) frictionally retained on said ram rod (62) and movable in unison with said punch (27) during a portion of the stroke of said punch (27), said holder (54) including means (57) for holding the one fastener element (A) in front of said punch (27), further including a retainer mechanism (35) incorporated in said ram (64) and lockingly engageable with said holder (54) for retaining said holding means (57) in an element-receiving position when said punch (27) is in an uppermost standby position. An apparatus according to claim 7, said tubular holder (54) having a radially outwardly projecting abutment (56), said retainer mechanism (35) including a vertically elongate hook (65) pivotably mounted on said ram (64) and having a locking projection (70) disposed below said abutment (56) and lockingly engageable with the latter when said punch (27) arrives at said uppermost standby position, and spring means (66) acting between said ram (64) and said hook (65) for urging the latter to turn in a direction to move said locking projection radially inwardly of said tubular holder (54). An apparatus according to claim l, further including a chute (22) supported by said frame (20) for supplying the one fastener element (A) to said first passage (37), and a gate unit (36) supported on said frame (20) and including a slide block (l07) extending along said first feed passage (37), said slide block (l07) being movable in a direction parallel to said first feed passage (37) between a first position in which said slide block (l07) is disposed in confronting relation to a discharge end of said chute (22) so as to define therebetween said first feed passage (37), and a second position in which said slide block (l07) is disposed out of confrontation with said discharge end, said slide block (l07) being normally held in said first position. An apparatus according to claim 9, said gate unit (36) further including a detent assembly (ll2, ll3) for retaining said lide block (l07) in said first and second positions against displacement. An apparatus according to claim l0, said detent assembly including a pair parallel spaced grooves (ll2) defined in said frame (20) and extending in a direction transverse to said first feed passage (37), and at least one spring-biased ball (ll3) mounted in said slide block (l07) and snappingly receivable in said grooves (ll2). An apparatus according to claim 9, said gate unit (36) further including a knob (ll2) attached to said slide block (l07). An apparatus according to claim 9, said chute (22) having a retaining recess (l05) extending in said discharge end, said guide block (l07) having a groove (l20) normally facing toward said discharge end of said chute (22), said gate unit (36) further including a retainer finger (ll5) slidably mounted in said slide block (l07) and having a retaining recess (ll7) opening toward said retaining recess, and a leaf spring (ll9) acting between said slide block (l07) and said retainer finger (ll5) to urge the latter toward said discharge end of said chute (22). An apparatus according to claim l, further including an optical position indicator (34) movably supported by said frame (20) for indicating a position on the garment fabric (C) where the two fastener elements (A, B) are to be attached, and a third drive mechanism (33) operatively connected with said position indicator (34) and movable under the control of said first pusher mechanism (28) for reciprocating said position indicator (34) toward and away from the path of movement of said punch (27) in such a manner that retracting movement of said position indicator (34) begins slightly after the start of retracting movement of said first pusher (85). An apparatus according to claim l4, said third drive mechanism (33) including a slide bar (l23) slidably supported on said frame (20) and supporting thereon said position indicator (34), a follower member (l26) carried on said slide bar (l23), and spring means (l24) acting between said frame (20) and said slide bar (l23) to urge the latter in one direction to advance said position indicator (34), said first pusher mechanism including an actuating lever (82) pivotably supported on said frame and pivotably connected at its one end to a rear end of said first pusher (85) to reciprocate said first pusher (85), said actuating lever (82) being normally spaced from said follower member (l26) and engageable with the latter to move said slide rod (l23) in the opposite direction against the bias of said spring means (l24) during pivotal movement of said actuating lever (82) in a direction to retract said first pusher (85). An apparatus according to claim l, said second drive mechanism (30) including a fluid-pressure actuator (l64) having a piston rod (l68), said second pusher mechanism (32) including a cam block (l69) connected to said piston rod (l68) of said second drive mechanism (30), and a pivot lever (l7l) urged against a cam surface (l74, l75) on said cam block (l69) and operatively connected to said second pusher (l40) for reciprocating the latter in response to the reciprocating movement of said piston rod (l68), said cam surface (l74, l75) being profiled such that during a portion of movement of said piston rod (l68) from said actuator (l64) adjacent the fully retracted position of said piston rod (l68), said cam surface (l74) turns said pivot lever (l7l) to reciprocate said second pusher (l40), while during a portion of movement of said piston rod (l68) from said actuator (l64) adjacent the fully extended position of said piston rod (l68), said cam surface (l75) does not turn said pivot lever (l7l) to interrupt reciprocating movement of said second pusher (l40). An apparatus according to claim l6, said cam surface including a sloping cam surface (l74) and a flat cam surface (l75) extending contiguous to said sloping cam surface (l74).

Inventors: TAGA, YUKIO
Applicants: YOSHIDA KOGYO K.K.
Application year: 1987
Main classification: A41H37
IPC codes: A41H37, A44B19