Transfer device for transfer presses

Abstract: A transfer press includes a plurality of regularly spaced upper and lower dies (38 and 39) which together define a process line and parallel guides (40 and 41) on opposite sides of the process line. A plurality of interconnected, regularly spaced trolleys (42) are movably supported on the guides (40,41) and connected to first drive means (64,67) arranged to reciprocate the trolleys on the guides. Workpiece supporting means (60) are vertically movably mounted on the trolleys and extend perpendicular to the process line and are connected to second drive means (75,68,71) arranged to reciprocate the workpiece supporting means vertically on the trolleys. Workpiece holding means constituted by vacuum cups (61) are carried by each workpiece supporting means and arranged to engage a workpiece (62) and to hold it whilst moving along the process line.

Description: The present invention relates to a transfer device for a transfer press and to a method of transferring workpieces through a transfer press. A transfer device of the type according to the first part of claim 1 is known from JP-A-61-226128. Prior to the detailed description of the present invention, a conventional transfer device will be described with reference to Figures 1 and 2 so as to explain the technical problems associated with it which the present invention aims to solve. Figures 1 and 2 are a perspective view of a known transfer device and a further similar view illustrating the operation of the device whilst Figure 3 is a side view of the drive system for the device which includes a pair of vertically movable frames 1 and 2 (referred to hereinafter as "lift frames") disposed on opposite sides of a die array comprising a plurality of dies and extending parallel to one another and to the direction of the process line. A plurality of movable stands 3 and 4, which are movable in the direction of the process line, are mounted on the lift frames 1 and 2 and interconnected such that the distance between the adjacent pairs of movable stands 3 and 4 is maintained substantially equal to the distance between the adjacent die or process stations A and B. The movable stands 3 and 4 are drivingly coupled to a drive system (not shown) such that they may be reciprocated in the direction of the process line. A pair of supporting stands 5 and 6, which are reciprocably movable toward or away from each other in the direction of the process line is mounted on the pair of movable stands 3 and 4 and cross bars 7 and 8 are mounted on the opposing supporting stands 5 and 6, respectively. A plurality of vacuum cups 9, which can releasably engage and retain a blank sheet by suction are mounted on the cross bars 7 and 8. Reference numeral 10 represents pressed articles or workpieces. After the articles 10 have been pressed at the upstream die station A, the lift frames 1 and 2 are moved upwardly. While the cross bars 7 and 8, which were maintained at the retracted positions adjacent to the intermediate position C, are moved away from each other, the movable stands 3 and 4 are moved to the station A. Thereafter the lift frames 1 and 2 are moved downwardly to lower the cross bars 7 and 8 toward the articles 10 at the station A and then the vacuum cups 9 are actuated to cause the articles 10 to engage the cross bars 7 and 8. Next the lift frames 1 and 2 are moved upwardly and the movable stands 3 and 4 are moved in the downstream direction to transfer the articles 10 to the downstream die station B. Then the lift frames 1 and 2 are lowered and the vacuum cups 9 are released so that the articles 10 are lowered and placed at the downstream station B. Thereafter the lift frames 1 and 2 are again moved upwardly. While the cross bars 7 and 8 are caused to move towards each other, the movable stands 3 and 4 are moved back to the intermediate position C. Then the lift frames 1 and 2 are lowered while the cross bars 7 and 8 are retracted and the articles 10 are further pressed at the downstream die station B. Thus, as a result of the periodic movements of the lift frames 1 and 2, the movable stands 3 and 4 and the supporting stands 5 and 6, the cross bars 7 and 8 are caused to move vertically, transfer the articles 10 and move toward or away from each other so that all the articles 10 are sequentially transferred in the downstream direction from station to station and automatically pressed at a plurality of die or process stations. The transfer device described above includes, as best shown in Figure 3, a first drive device for reciprocating the movable stands 3 and 4 in the direction of the process line and a third drive device for reciprocating the supporting stands 5 and 6 in synchronism with the movement of the movable stands 3 and 4 and causing them and thus the cross bars 7 and 8 to move toward or away from each other on the movable stands 3 and 4. More specifically, the first drive device 1 comprises a horizontal rack 11, which is coupled to a power source (not shown) to be moved horizontally, a pinion 12 in mesh with the rack 11 and a vertical rack 13 in mesh with the pinion 12 with the upper end thereof being securely connected to an associated lift frame 1 or 2, whereby the lift frames 1 and 2 are moved vertically when the rack 11 is moved horizontally. The second drive device comprises a carriage 15 which is located at one end of the lift frames 1 and 2 and connected to the movable stands 3 and 4 by a connecting rod 14 and is reciprocable in the direction of the process line, and a feed lever 20 whose upper portion is vertically slidable in a vertical groove 16 formed in the carriage 15, and which is pivoted about a pivot pin 17 and carries a cam follower 18 at its lower end in contact with a feed cam 19. When the feed cam 19 is rotated, the feed lever 20 is caused to pivot about the pivot pin 17 whereby its upper portion slides within the groove 16. The swinging movement of the feed lever 20 is translated into movement of the carriage 15 in the direction of the process line and thus also of the movable stands 3 and 4. The third drive device comprises a cam plate 27 attached securely to the lift frames 1 and 2 and having a closed-loop cam surface consisting of a downwardly directed cam surface 21, a reversal cam surface 22, an upwardly inclined cam surface 23, an upwardly directed cam surface 24, an upwardly inclined cam surface 25 and a second reversal cam surface 26 and an inverted T-shaped lever 33 which is pivotally connected at the mid-point between its lower ends to the carriage 15 by a pivot pin 28 and at one lower end has a cam follower 29 in rolling contact with the closed-loop cam surface (21-26). Connected to the other lower end of the lever 33 is a bias cylinder 30 for pressing the cam follower 29 against the cam surfaces 21-26. The lever 33 is connected to a push-pull rod 32, one end of which is slidable in an arcuate groove 31 formed in the upper end portion of the lever 33, as will be described in more detail below. The push-pull rods 32 extend through the movable stands 3 and 4 such that they are reciprocable in the direction of the process line to impart a driving force to the supporting stand 5 and to the supporting stand 6 through a rack 34, a pinion 35 and a horizontal rack 36, whereby swinging movement in the direction of the process line of the lever 33 in unison with the carriage 15 is translated into movement of the push-pull rods 32 in the direction of the process line, thereby causing the supporting stands 5 and 6 on the movable stands 3 and 4 to move toward or away from each other so that the cross bars 7 and 8 are also forced to move toward or away from each other. A cylinder 37 changes the displacement of the push-pull rod 32 when the pivotal point of the push-pull rod 32 with respect to the lever 33 is changed to swing the lever 33. The transfer method and device described above have various technical problems. Firstly, a substantial driving force is required to vertically move the lift frames 1 and 2 which are both long and very heavy. Furthermore, it is impossible to increase the speed of the process line in order to increase productivity since such a speed increase would cause vibrations or oscillations of the lift frames 1 and 2 when the articles 10 are being transferred resulting in dropping of the articles 10 from the vacuum cups 9. Moreover, the movement of the cross bars 7 and 8 toward and away from one another cannot be increased by means of the cam plate 27 because of its complicated construction of the cam plate 27 for causing the bars 7 and 8 to move toward or away from each other. It is therefore an object of the present invention to make the lift component parts of a transfer device both compact and light, thereby decreasing the driving force, preventing vibrations or oscillation and making the transfer drive system of simple construction. According to the present invention a transfer device for a transfer press comprises guide means which, in use, extend parallel to and on each side of the process line of the press, the device comprising a plurality of interconnected, regularly spaced trolleys reciprocably supported on the guide means, workpiece supporting means mounted on each trolley and workpiece holding means carried by each workpiece supporting means and arranged to engage a workpiece and to hold it whilst moving along the process line characterised in that each trolley supports only one workpiece supporting means which is vertically reciprocably mounted on the trolley, and the trolleys on each guide means are regularly spaced in the direction in which the guide means extend, the workpiece holding means being associated in pairs on each workpiece supporting means and extending therefrom in opposite directions and mounted so as to be relatively movable in opposite directions parallel to the direction in which the guide means extend. Thus in the transfer device of the present invention the workpieces are moved by moving the workpiece holding means vertically with respect to the trolleys and then moving the trolleys along the guide means and the guide means are maintained stationary, at least whilst the workpieces are being moved. In the prior constructions the guide means are themselves moved vertically, but since the workpiece supporting means can inherently be very much smaller and lighter than the guide means this enables the lifting gear to be very much smaller and cheaper than previously and also enables it to operate more rapidly thereby increasing the productivity of the press without risking vibration which might result in the workpieces becoming dislodged from the workpiece holding means. Since the workpiece holding means are reciprocably mounted on the supporting means the trolleys may be made very light so that the speed of the process line is further increased. In practice, the trolleys will be spaced apart by a predetermined distance equal to the spacing of the work stations, that it to say, the die assemblies which define the process line, of the transfer press. Each workpiece is moved by only a single workpiece supporting means and the workpiece supporting means are thus spaced apart in the direction of the process line by the same distance. The workpiece supporting means may extend upwardly or laterally from the trolleys or be suspended below the trolleys. Although the guide means are maintained stationary whilst the workpieces are being moved it may nevertheless be desirable to be able to adjust their height and thus the transfer device may include height adjusting means arranged to move the guide means vertically. The drive system for the transfer device may take many forms, but in the preferred embodiment this drive system includes a transfer lever mounted to pivot about a pivot shaft, a transfer cam arranged to engage the transfer lever and to cause it to pivot reciprocally, a lift link rotatably carried by a shaft which is parallel to the pivot shaft and it rotatably connected to the transfer lever, a lift lever rotatably carried by the said pivot shaft, a lift cam arranged to engage the lift lever and to cause it to pivot reciprocally, a lift rod connecting the lift lever and the lift link and extending perpendicular to the pivot shaft and being of a length substantially equal to the distance between the said shaft and the said pivot shaft, a first drive means for reciprocating the trolleys on the guide means including the said shaft and a second drive means for vertically reciprocating the workpiece supporting means on the trolleys including a portion of the lift link remote from the said shaft. Alternatively, the drive system may comprise a first motor connected to a trolley and a second motor connected to a vertically movable bar connected to the workpiece supporting means. The drive system may further comprise a third motor connected to a distance adjustment bar connected to the workpiece supporting means. Finally, the present invention also embraces a method of transferring workpieces through a transfer press comprising engaging the workpieces by means of workpiece holding means associated in pairs on workpiece supporting means and extending therefrom in opposite directions and mounted so as to be relatively movable in opposite directions parallel to the direction in which the workpieces are transferred, the supporting means in turn being carried by trolleys running on guide means situated on each side of the process line of the press defined by a plurality of regularly spaced die assemblies, raising the workpiece supporting means with respect to the trolleys, advancing the trolleys by a distance equal to the spacing of the die assemblies, lowering the workpiece supporting means, releasing the workpieces, raising the workpiece supporting means, returning them to their original position and then repeating the procedure whilst maintaining the guide means stationary, at least while moving the trolleys. Further features and details of the invention will be apparent from the following description of certain specific embodiments of the invention which is given by way of example with reference to Figures 4 to 27 of the accompanying drawings, in which:- Figure 4 is a top view of a transfer press which is novel over the prior art cited herein, but which is not in accordance with the present invention; Figure 5 is a side view thereof; Figure 6 is a view on an enlarged scale of a trolley shown in Figure 4; Figure 7 is a front view thereof; Figure 8 is a side view of the transfer drive device used in the transfer press shown in Figure 4; Figure 9 is an exploded perspective view thereof; Figure 10 is a side view of a first modification of the transfer press of Figures 4 to 9; Figure 11 is a side view of a second modification of the transfer press of Figures 4 to 9; Figure 12 is a top view of a first preferred embodiment of a transfer device in accordance with the present invention; Figure 3 is a side view thereof; Figure 14 is a side view on an enlarged scale of a trolley used in the first embodiment of the present invention shown in Figure 12; Figure 15 is a perspective view on an enlarged scale of a cross bar of a trolley shown in Figure 12; Figure 16 is a top view of a modification of the first embodiment of the present invention; Figure 17 is a side view of a second preferred embodiment of a transfer device in accordance with the present invention; Figure 18 is an enlarged view a trolley used in the second embodiment shown in Figure 17; Figure 19 is a front view thereof; Figure 20 is a view used to explain the transfer drive device used in the second embodiment shown in Figure 17; Figure 21 is a partial side view of a third embodiment of the present invention: Figure 22 is a plan view thereof; Figure 23 is a diagram showing the hydraulic circuit used in the third embodiment shown in Figure 22; Figure 24 is a plan view of a first modification of the third embodiment; Figure 25 is a side view thereof; Figure 26 shows a second modification of the third embodiment; and Figure 27 is a side view thereof. In the following description, the terms "distance adjustment...", such as distance adjustment bar, distance adjustment lever, are used in relation to parts used in the mechanism for causing a pair of cross bars 60 to move toward or away from each other, thereby adjusting the distance between them. Referring firstly to Figures 4 to 9, a transfer press is described which has been devised by the inventors of the present invention and is novel over the prior art mentioned herein, but is not in accordance with the present invention. The transfer press includes a plurality of sets of upper and lower dies 38 which are regularly spaced apart from each other in the direction of the process line and a pair of parallel guides 40 and 41 extends along opposite sides of the process line. A plurality of trolleys 42, which are movable in the direction of the process line, is mounted on the guides 40,41 and interconnected by means of connecting bars 43 such that the distance between the adjacent trolleys 42 is maintained substantially equal to the distance between the adjacent upstream and downstream die sets 38 and 39. The most upstream or downstream trolley 42 is connected by a transfer bar 44 to a transfer drive system, that is to say a system for driving a transfer device in accordance with the present invention which will be described below, so that in response to the reciprocating motion of the transfer bar 44 in the direction of the process line, all the interconnected trolleys 42 are reciprocated in the direction of the process line simultaneously. A lift bar 45, which is reciprocated in the direction of the process line by the transfer drive system to be described below, slidably extends through each trolley 42 and the portions of the lift bar 45 which are located within the trolleys 42 are formed with a rack 46. A pinion 47 in mesh with the rack 46 and a pinion 48 which rotates with the pinion 47 but is not in mesh with the rack 46 are rotatably mounted on each trolley 42. Vertical racks 49 and 50 in mesh with the pinions 47 and 49, respectively extend vertically through the trolley 42 and beyond the top thereof. A guide plate 51 which extends in the direction of the process line is securely joined to the upper ends of the vertical racks 49 and 50 such that it is moved vertically in unison with the reciprocal motion of the lift bar 45 in the direction of the process line. A distance adjustment bar 52, which is reciprocated in the direction of the process line by the transfer drive system to be described below, extends slidably through each trolley 42 and the portions of the bar 52 located within the trolleys 42 are formed with a rack 53. A pinion 54 in mesh with the rack 53 is rotatably mounted within each trolley 42. A horizontal rack 55 in mesh with the pinion 54 is mounted within the trolley 42 such that the rack 55 is movable in the direction of the process line. Two supporting stands 56 and 57 are mounted on the guide plate 51 such that they are moveable in the direction of the process line. One supporting stand 56 is supported by the upper end portion of a vertical rod 58 which slidably extends through the stand 56 and the lower end of the vertical rod 58 is securely joined to the horizontal rack 55. The other supporting stand 57 is supported by the upper end portion of a vertical rod 59 which slidably extends through the stand 57 and the lower end of the vertical rod 59 is securely joined to the distance adjustment bar 52. Thus, in response to the reciprocal motion of the distance adjustment bar 52 in the direction of the process line, the supporting stands 56 and 57 are caused to move toward or away from each other by the pinion 54, the horizontal rack 55 and the vertical rods 58 and 59. Work supporting means such as cross bars 60 extend between the opposing supporting stands 56 and 57 on the guides 40 and 41 and work clamping or holding means such as vacuum cups 61 adapted to releasably engage the workpieces or articles by suction are attached to each cross bar 60 at a height corresponding to the height of the upper and lower dies 38 and 39 and the workpieces 62. The transfer drive system is illustrated in Figures 8 and 9 and includes an L-shaped transfer lever 64 which is pivoted about a pivot pin 63 so as to be swingable in the direction of the process line and has at its lower end a cam follower 65 which contacts the cam profile surface of a transfer cam 67 carried by a cam shaft 66 so that upon rotation of the transfer cam 67 the transfer lever 64 is caused to swing about the pivot pin 63 by the cam follower 65. As best shown in Figure 9, one end of a lift lever 68 and of a distance adjustment lever 69 are rotatably carried by the pivot pin 63 and the other ends of the levers 58 and 69 carry respective cam followers 70, which in turn are pressed against a lift cam 71 and a distance adjustment cam 72, respectively, carried by a cam shaft 73. A horizontal shaft 74 extends through the upper end portion of the transfer lever 64 and a V-shaped lift rocker 75 is rotatably carried by one end of the horizontal shaft 74 while a V-shaped distance adjustment rocker 76 is rotatably carried by the other end of the horizontal shaft 74. A lift rod 77 which is parallel with and equal in length to the line connecting the pivot shaft 63 and the horizontal shaft 74 has its upper and lower ends pivotally connected to one end of the transfer rocker 75 and to a point between the ends of the lift lever 68, respectively, whereby a parallelogram linkage is defined. In like manner, the upper and lower ends of the distance adjustment rod 78 are pivotally connected to one end of the distance adjustment rocker 76 and a point between the ends of the distance adjustment lever 69, whereby a parallelogram linkage is also defined. Therefore when the transfer cam 67 swings the transfer lever 64, the lift rocker 75 can be swung independently by the lift cam 71, the lift lever 68 and the lift rod 77 while the distance adjustment rocker 76 can also swing independently by the action of the distance adjustment cam 72, the distance adjustment lever 69 and the distance adjustment rod 78. The upper end of the transfer lever 64 is connected to the downstream end of the transfer bar 44 by a connecting rod 79. Alternatively, the transfer bar 44 may be omitted and the transfer lever 64 may be directly connected to the most upstream or downstream trolley 42. The other end of the lift rocker 75 is connected to the downstream end of the lift bar 45 by a connecting rod 80. The other end of the distance adjustment rocker 76 is connected to the downstream end of the distance adjustment bar 52 by a connecting rod 81. The mode of operation of the transfer press described above is as follows: When the transfer cam 67 swings the transfer lever 64, the connecting rod 79 and the transfer bar 44 are moved in the direction of the process line so that the trolleys 42 interconnected by the connecting bars 43 in the manner described above are caused to reciprocate in unison in the direction of the process line. When the lift cam 71 swings the lift lever 68 with respect to the transfer lever 64 while the lever 64 is swinging, the lift rocker 75 is caused to swing by the lift rod 77 so that the connecting rod 80 and the lift bar 45 caused to move in the direction of the process line with respect to the transfer bar 44 and consequently the cross bars 60 are moved vertically by the pinions 47 and 48, the vertical racks 49 and 50 and the guide plates 51. In like manner, when the distance adjustment cam 72 causes the distance adjustment lever 69 to swing with respect to the transfer lever 64 while the lever 64 is swinging, the distance adjustment rocker 76 is caused to swing by the distance adjustment rod 78 so that the connecting rod 81 and the distance adjustment bar 52 connected thereto are caused to move in the direction of the process line with respect to the transfer bar 44. As a result, the pairs of cross bars 60 are moved toward and away from each other by the pinions 54, the horizontal racks 55, the vertical rods 58 and 59 and the supporting stands 56 and 57. As the cross bars 60 are reciprocated in the direction of the process line the vacuum cups are actuated and deactuated at the appropriate times to engage and release the workpieces. The various movements are so combined and timed that the workpieces 62 are sequentially transferred toward the downstream direction of the process line and pressed at each press station. The vertical stroke and the horizontal stroke of the motion of the cross bars 60 and the timing of the vertical and horizontal motion thereof can be artibrarily selected by changing the cam profiles of the lift cam 71 and the distance adjustment cam 72, which selection is independent of the stroke of the trolleys 42 which in turn is dependent upon the transfer lever 64. In the event that no relative movement of the parts of cross bars toward or away from each other is needed due to the specific shape and/or materials of the workpieces 62, the cam profile of the distance adjustment cam 72 may be shaped to maintain the angle between the distance adjustment lever 69 and the transfer lever 64 at a constant predetermined value during the swinging motion. The transfer device is so designed and constructed that the trolleys 42 reciprocate along the guides 40 and 41 which are vertically fixed during transfer of the workpieces 62. During such transfer, only the work supporting means comprising the guide plates 51, the supporting stands 56 and 57 and the pairs of cross bars 60 supported on the trolleys 42 are permitted to move vertically. Figure 10 shows a first modification of the transfer press described above, in which the transfer lever 64 and the transfer bar 44 are connected through a carriage 82 movable in the direction of the process line along the guide 40; the lift rocker 75 and the lift bar 45 are connected through a carriage 83 movable on the carriage 82 in the direction of the process line; and the distance adjustment rocker 76 and the distance adjustment bar 52 are connected through a carriage 84 movable on the carriage 82 in the direction of the process line. Figure 11 shows a second modification in which the transfer bar 44, the lift bar 45 and the distance adjustment bar 52 are formed with racks 127, 128 and 129, respectively, which are in mesh with pinions 130, 131 and 132, respectively, carried by the drive shafts of motors, e.g. servomotors 133, 134 and 135, respectively, so that when these motors 133, 134 and 135 are energised, the transfer bar 44, the lift bar 45 and the distance adjustment bar 52 are reciprocated in the direction of the process line. The first embodiment of the present invention is illustrated in Figures 12 to 15 and is generally similar to the first embodiment with the exception of the following features: The cross bars 60 are arranged singly rather than in pairs and are vertically movably supported by an associated pair of opposing trolleys 42. A shaft 88 extends through each cross bar 60 along the longitudinal axis thereof and is rotatable by a motor 87. A plurality of spaced pinions 89 are mounted on the shaft 88. Each pinion 89 is in mesh with a respective pair of upper and lower racks 90 and 91 extending in the direction of the process line and vacuum cups 61 are attached to the outer ends of the racks 90 and 91 remote from the pinions 89. When the motor 87, e.g. a servomotor, is energised, the upper and lower racks 90 and 91 are moved in opposite directions by the shaft 88 and the pinions 89 so that the vacuum cups 61 are moved toward or away from the adjacent upstream and downstream vacuum cups. It will be appreciated that the drive mechanisms described with reference to Figure 6 to 9, Figure 10 and Figure 11 are applicable to the first embodiment, with the exception of those parts whose function is to reciprocate the cross bars 60 with respect to each other, i.e. the distance adjustment bar 52, rack 53, pinion 54 rack 55, and stands 56 and 57. Thus, the drive mechanisms described may be used in the first embodiment to reciprocate the trolleys and to vertically reciprocate the workpiece holding means. As shown in Figure 13, the guide plates 51 are omitted in the first embodiment, since they are for obvious reasons, not required. The lift mechanism is both compact and light and only a small amount of power is needed to move the cross bars 60 vertically. No vibrations or oscillations occur during the operation of the lift mechanism so that the vacuum cups 60 positively retain the workpieces 62 and do not release or drop them. Thus, it becomes possible to increase the speed of the process line, thereby improving productivity. The trolleys 42 can also be made very light so that the speed of the process line can be increased. The transfer drive system of the first embodiment is of simple construction and the vertical stroke of the cross bars 60 can be freely selected, and the available stroke is longer in length. Furthermore, the component parts are connected with pin or pivot joints so that any play between them can be reduced to a minimum and therefore the pressing operation can be carried out with a high degree of dimensional accuracy. Figure 16 shows a modification of the first embodiment in which a pair of spaced elongate slots 93 are formed in and extend in the longitudinal direction of each cross bar 60. Pins 94 and 95 are slidably fitted into the slots 92 and 93, respectively, and one pin 94 is connected to the piston rod of a piston/cylinder unit 96 which is extendable and retractable in the longitudinal direction of the cross bar 60. Two links of a pantograph 97 are joined to the pin 93 while the remaining two links of the pantograph are joined to the pin 94, i.e. two opposing apexes of the pantograph or parallelogram 97 are connected to the pins 93 and 94. The remaining two opposing apexes of the pantograph 97 are joined to the vacuum cups 61. When the cylinder 96 is extended or retracted, the pins 94 and 95 are displaced in the slots 92 and 93, respectively, so that the pantograph 97 is driven to move the vacuum cups 61 towards or away from each other. This modification can also attain the same effects and advantages as the first embodiment. In Figure 16, reference numeral 98 represents a link connecting the pins 94;99, an expandable-and-retractable diagonal member connecting the vacuum cups 61; and 100, a guide formed through the cross bar 60 for guiding the diagonal member 99. The second embodiment of the present invention is illustrated in Figures 17 to 20 and is again generally similar in construction to the first embodiment except that the guide 40' is disposed substantially in coplanar relationship with or at a position higher than the upper surface of the upper die 38 when the die 38 is removed and placed over the lower die 29 during the replacement of the upper and lower dies 38 and 39 in a press (not shown) (In Figure 17, the guide 40' is shown as being disposed at a position higher than the upper end of the stroke of the upper die 38). The cross bars 60' are securely attached to the lower ends of respective vertical racks 49. A gear box 101 mounted on the most downstream trolley 42 is connected to a rod 79 extending from the upper end portion of the transfer bar 64. A rod 80 extends from the upper end portion of the lift link 75 and is connected to a sector gear 104 which transmits the driving force to the lift bar 45 through gears 102 and 103 mounted in the gear box 101. Reference numeral 105 designates a bolster upon which the lower dies 39 are mounted in replacement of the upper and lower dies 38 and 39; 106, rollers attached to the trolley 42; 107, a cylinder for adjusting the height of the guide 40'; and 108, a clamping cylinder. The vacuum cups 61 are indirectly mounted on the cross bars 60' for distance adjustment movement, as in the first embodiment. The second embodiment achieves the same advantages as the first embodiment and thus the speed of the process line can be increased so that productivity can be improved. Furthermore, the guide 40' is disposed at a relatively high position so that when maintaining or replacing the upper and lower dies 38 and 39, it is not necessary to lift and retract the guide 40' so that the replacement or maintenance of the dies can be accomplished relatively rapidly whereby productivity can be further improved. Figures 21 to 23 show a third embodiment of the present invention which is generally similar in construction to all the preceding embodiments except that uprights 136 for the transfer presses have vertically extending guide members 137 along which guide bodies 138 are slidable. The guide bodies 138 are attached to the pair of guides 40 and 41 and vertically movably support the latter on the uprights 136. The uprights 136 and the guides 40 and 41 are connected respectively by cylinders 139 and 140 which serve as height adjustment means. The cylinders 139 and 149 communicate with a synchronism cylinder 150 which comprises two cylinder portions 147 and 148, as shown in Figure 35. More specifically, the cylinder portion 147 has a piston 141 and a liquid-pressure chamber 143 and 144 on each side of the piston 141; in like manner, the cylinder portion 148 has a piston 142 and a liquid-pressure chamber 145 and 146 on each side of the piston 142. The cylinder portions 147 and 148 are connected in a series by a rod 149 to provide the synchronism cylinder 150. The liquid-pressure chambers 143 and 145 of the cylinder portions 147 and 148 communicate through flow passages 151 and 152 with the rod-side chambers of the cylinders 139 and 140. The head-side chambers of the cylinders 139 and 140 communicate through a flow passage 153 with a directional control valve 154 which in turn communicates with the liquid-pressure chamber 148 of the synchronism cylinder 150 through a flow passage 156 which includes a pilot check valve 155 and communicates at its pilot port with the flow passage 153. The direction control valve 154 further communicates with a pump 158 as well as a tank 157. The trolleys and the work supporting means are omitted from Figures 21 and 22 for the sake of simplicity. The third embodiment can of course attain the same effects and advantages as any of the preceding embodiments. Moreover, in this embodiment, during or prior to the pressing operation the height of the guides 40 and 41 can be adjusted in accordance with the height of the dies 38 and 39 and/or the height of the workpieces to be transferred by means causing the cylinders 139 and 140 to extend or retract. When exchanging the dies 38 and 39 or maintaining the transfer presses, the guides 40 and 41 can be retracted to non-interfering position. More specifically, the guides 40 and 41 may be lifted by feeding working liquid from the tank 175 through the directional control valve 154 and the synchronism cylinder 150 to the rod-side chambers of the cylinders 139 and 140 to retract the cylinders 139 and 140; on the other hand, the guides 40 and 41 may be lowered by feeding the working liquid to the head-side chambers of the cylinders 139. The chambers 143 and 145 of the synchronism cylinder 150 are arranged to change in volume in unison so that the pair of guides 40 and 41 can be synchronously height-adjusted. The pilot check valve 155 in the flow passage 156 serves to prevent back flow from the synchronism cylinder 150 so that the guides 40 and 41 can be maintained at the desired height. When the guides 40 and 41 are to be lowered, the working liquid in the flow passage 153 acts on the pilot port of the pilot check valve 155 to open the latter so that the working liquid can be discharged from the flow passage 156 to the tank 158. Figures 24 and 25 show a first modification of the third embodiment in which, instead of the cylinders, jacks 161 are employed as the height of adjusting means which are driven by motors 159 and associated gearing 160. Figures 26 and 27 show a second modification of the third embodiment which employs pinions 162 and vertically extending racks 163 in mesh with the pinions 162 instead of the jacks in the first modification. The pinions 162 are connected to the gearing 160 while the rack 163 is connected at its upper end to the corresponding guide 40 or 41. The first and second modification can attain the same effects and advantages as the third embodiment. It is to be understood that the present invention is not limited to the embodiments and their modifications described above and that further various modifications may be effected. The number of the work supporting means may be three or more.

Claims: A transfer device for a transfer press comprising guide means (40,41) which, in use, extend parallel to and on each side of the process line of the press, the device comprising a plurality of interconnected, regularly spaced trolleys (42) reciprocably supported on the guide means (40,41), workpiece supporting means (60) mounted on each trolley (42) and workpiece holding means (61) carried by each workpiece supporting means (60) and arranged to engage a workpiece and to hold it whilst moving along the process line characterised in that each trolley (42) supports only one workpiece supporting means (60) which is vertically reciprocably mounted on the trolley (42), and the trolleys on each guide means (40,41) are regularly spaced in the direction in which the guide means (40,41) extend, the workpiece holding means (61) being associated in pairs on each workpiece supporting means (60) and extending therefrom in opposite directions and mounted so as to be relatively moveable in opposite directions parallel to the direction in which the guide means (40,41) extend. A device as claimed in claim 1 including height adjustment means (136-140; 159-161; 162,163) arranged to move the guide means (40,41) vertically. A device as claimed in any one of the preceding claims including a drive system comprising a transfer lever (64) mounted to pivot about a pivot shaft (63), a transfer cam (67) arranged to engage the transfer lever (64) and to cause it to pivot reciprocally, a lift link (75) rotatably carried by a shaft (74) which is parallel to the pivot shaft (63) and is rotatably connected to the transfer lever (64), a lift lever (68) rotatably carried by the said pivot shaft (63), a lift cam (71) arranged to engage the lift lever (68) and to cause it to pivot reciprocably and a lift rod (77) connecting the lift lever (68) and the lift link (75) and extending perpendicular to the pivot shaft (63) and being of a length substantially equal to the distance between the said shaft (74) and the said pivot shaft (63), a first drive means for reciprocating the trolleys on the guide means including the said shaft (74) and a second drive means for vertically reciprocating the workpiece supporting means on the trolleys including a portion of the lift link (75) remote from the said shaft (74). A method of transferring workpieces through a transfer press comprising engaging the workpieces by means of workpiece holding means (61) associated in pairs on workpiece supporting means (60) and extending therefrom in opposite directions and mounted so as to be relatively moveable in opposite directions parallel to the direction in which workpieces are transferred, each supporting means (60) in turn being carried by its respective trolley (42) running on guide means (40,41) situated on each side of the process line of the press defined by a plurality of regularly spaced die assemblies (38,39), raising the workpiece supporting means (60) with respect to the trolleys (42), advancing the trolleys (42) by a distance equal to the spacing of the die assemblies, lowering the workpieces supporting means (60), releasing the workpieces, raising the workpiece supporting means (60), returning them to their original position and then repeating the procedure whilst maintaining the guide means (40,41) stationary, at least while moving the trolleys (42).

Inventors: ARIKAWA TAKAMASA, ISHIDA NOBUJI, IURA TAKAO, NAKAMURA KENJI, ONOGI KATSUYUKI, SATO IZUMI, SUDO MITSUO, TAKAHASHI YOSHIO, ARIKAWA, TAKAMASA, ISHIDA, NOBUJI, IURA, TAKAO, NAKAMURA, KENJI, ONOGI, KATSUYUKI, SATO, IZUMI, SUDO, MITSUO, TAKAHASHI, YOSHIO
Applicants: ISHIKAWAJIMA HARIMA HEAVY IND, ISHIKAWAJIMA-HARIMA  JUKOGYO KABUSHIKI KAISHA
Application year: 1988
Main classification: B21D43
IPC codes: B21D43