Can forming apparatus

Abstract: Object: To provide a can forming apparatus which is improved to remarkably suppress generation of noise and to avoid generation of defects such as dents and scratches on a can blank, thus effecting smooth deep drawing and ironing on the can blank without fail. Construction: The can forming apparatus has a pair of feed guides 51, 52 which are disposed on opposite sides of a path of feed of the can blank such as to partly project into the path and so as to temporarily hold a downwardly fed can blank C and to feed it again downward. The feed guides are provided with outer peripheral recesses which cooperate with each other in embracing the can blank therebetween and feeding it downward, and protrusions continuous from the recesses and adapted to press the can blank downward after the can blank is released from the recesses. A pair of leaf springs 60, 61 or a pair of rollers 55, 56 are disposed beneath the feed guides 51, 52 and urged to project into the path of feed so as to hold the can blank C before the can blank C is pressed downward by the protrusions after it is fed downward from the recesses.

Description: The present invention relates to a can forming apparatus in which a punch is reciprocatingly and linearly moved in a die bore so as to effect deep drawing and ironing (sometimes referred to as "DI processing", hereinafter) on a sheet of metal such as aluminum, steel or the like thereby forming a can of such a metallic material, as indicated in the preamble of claim 1. Description of the Related Arts: US-PS 3 771 344 discloses the utilization of fluid under pressure to strip a can body from a metal working punch at the conclusion of a metal working stroke. The punch includes a valve member which is maintained in a closed position covering a stripping fluid outlet in a valve chamber before the end of the metal working stroke. The valve member is maintained in the closed position by a pneumatic bias applied to the end of the valve member opposite the end of the punch. At the conclusion of the metal working stroke, the can body is domed upwardly toward the valve member so as to engage a projection extending from the valve member thereby forcing the valve member away from the end of the punch and opening the outlet in the valve chamber. This permits the stripping fluid to pass through the valve chamber outlet into contact with the interior of the container body thereby stripping the body from the punch. US-PS 4 996 865 (nearest state of the art) discloses the utilization of pressurized air to blow a can off of a punch at the end of a working stroke of the punch. At the end of a working stroke pressurized air is supplied from within a manifold surrounding a ram on which a punch is mounted at one end, through a circumferential slot and radial holes into a check valve, where the pressurized air flow is directed into plural axially extending passages formed downstream from the check valve in the center region of the ram and into an air tube extending through the ram into the punch in the working end. The punch is provided with a series of holes through which the pressurized air exits to blow the can off the punch. An object of the present invention is to provide a can forming apparatus which is improved such as to enable a higher can forming processing speed, while ensuring smooth separation of the body from the end of the punch. This object is achieved by a can forming apparatus as set forth in claim 1. In operation of a can forming apparatus according to the invention, the pinion having a pitch circle diameter equal to the pitch circle radius of the ring gear is made to revolve about the axis of the ring gear along the inner periphery of the ring gear in meshing engagement with the internal gear teeth of the ring gear. Consequently, the pinion makes a rotation about its own axis so that a predetermined point on the pitch circle of the pinion reciprocatingly and linearly move along a diametrical line of the ring gear, whereby the punch which is rotatably held on the above-mentioned pinion makes reciprocating linear motion. Meanwhile, the gas supplying means provided on the stationary part of the apparatus supplies a gas communication passage in the rotary member at a predetermined rotational angular phase of the rotary member, the gas being then supplied through the gas communication passage and via the axis of the pinion to the interior of the support shaft provided on the pitch circle of the pinion. The gas then further flows through the gas flow means to the gas blow-off hole in the punch so as to be discharged therefrom, thereby separating the can body from the end of the punch. It is therefore possible to attain a higher can forming processing speed, while ensuring smooth separation of the an body from the end of the punch. According to a preferred embodiment of the invention, the punch is supported by a fluid bearing so that a fluid pressure exists between the punch and the bearing to prevent direct contact therebetween during the reciprocating linear motion of the punch. This suppresses wear of the shaft supporting portion and ensures quick and stable can forming operation for a long period of time. BRIEF DESCRIPTION OF THE DRAWINGS Figs. 1a and 1b are a front elevational views of a feeding mechanism incorporated in an embodiment of the present invention; Fig. 2 is a plan view of the feeding mechanism shown in Fig. 1; Fig. 3 is a schematic illustration of the feeding operation performed by the feeding mechanism of Fig. 1; Fig. 4 is a plan view of left half part of a can forming apparatus as an embodiment of the present invention; Fig. 5 is a plan view of right half part of the can forming apparatus as an embodiment of the present invention; Fig. 6 is a front elevational view of left half part of a can forming apparatus as an embodiment of the present invention; Fig. 7 is a front elevational view of right half part of the can forming apparatus as an embodiment of the present invention; Fig. 8 is a side elevational view of the apparatus shown in Fig. 7; Fig. 9 is a sectional view of a gas discharging mechanism; Fig. 10 is a rear elevational view of the apparatus shown in Fig. 9; Fig. 11 is a plan view of a cup holder driving mechanism; Fig. 12 is a sectional view taken along the line XII-XII of Fig. 11; Fig. 13 is a front elevational view of the apparatus shown in Fig. 11; Fig. 14 is an illustration of the relationship between a ring gear and a pinion; Fig. 15 is an illustration of the pinion revolved through 90 ° from the position shown in Fig. 14; Fig. 16 is an illustration of the pinion revolved through 180 ° from the position shown in Fig. 14; and Fig. 17 is an illustration of the pinion revolved through 270 ° from the position shown in Fig. 14. Embodiments: An embodiment of the present invention will be described with reference to Figs. 1 to 17. Referring to these Figures, a can forming apparatus has a feeding mechanism 5 which feeds a cup-shaped can bank C into a bore 4a in a die 4 from the upper side of a stationary frame assembly 3, a cup holder 6 which is adapted to be inserted into the blank C so as to locate the blank C, an elongated punch 7 adapted to be driven into the cup holder 6 and the bore 4a of the die 4 so as to effect deep drawing and ironing on the blank C, a can bottom anvil 8 opposing to the punch 7 so as to cooperate with the punch 7 in forming the bottom of a can, a delivery mechanism 9 for delivering a can body B formed on the can bottom anvil 8 to the exterior, a punch driving mechanism 10 for causing a reciprocating linear motion of the punch 7, a pair of punch bearing mechanisms 20 for supporting and guiding the reciprocating punch 7, an air blow-off mechanism 30 for discharging air from the end of an air blow-off hole 7a formed in the center of the punch 7 so as to separate the can body 8 from the end of the punch 7, and a cup holder driving mechanism 40 which is driven by a motor 100 which also drives the punch driving mechanism 10 so as to cause a reciprocating linear motion of the cup holder 6 in synchronization with the movement of the punch 7. As shown in Fig. 1b the feeding-mechanism 5 includes the following parts or components: a chute 50 which extends vertically so as to allow the blank C to drop freely; a pair of feed guides 51, 52 which are disposed on the lower end of the chute 50 so as to be partly located in the path of feed, the feeder guides 51, 52 being carried by shafts 53, 54 for rotation in counter directions to each other; a pair of leaf springs 60, 61 or a pair of rollers 55, 56 disposed under the feed guides 51, 52 and partly located in the path of feed, and a stationary pocket 57 which receives the blank C fed by the leaf springs 60, 61 or by the rollers 55, 56. As shown in Fig. 3, the feed guides 51, 52 have substantially circular outer peripheral surfaces centered at the axes of rotation. As shown in Fig. 3, the peripheral surfaces of the feed guides 51, 52 are provided with dents or recesses 51a, 52a which, when the feed guides 51, 52 are driven for rotation, cooperate with each other in embracing the can blank C from left and right sides thereof so as to feed the blank C downward. In addition, protrusions 51b, 52b are formed on the peripheral surfaces of the feed guides 51, 52 so as to continue from the recesses 51a, 52a, so as to downwardly press the blank C fed from the space between the recesses 51a, 52a. During feeding of one can blank C, arcuate portions 51c, 52c of the peripheral surfaces of the feed guides 51, 52, formed between the protrusions 51b, 52b and the points at which the recesses 51a, 52a start, serve to support the next can blank C. As shown in Fig. 2, there are three interdigitating feed guides 51, 52, 51 which have axes parallel to each other, with the feed guide 52 partly received by a space between a pair of coaxial feed guides 51. As shown in Fig. 1a the leaf springs 60, 61 are disposed for rocking motion by means of tabular springs 60a, 61a, with ends 60b, 61b thereof being outwardly rounded, whereas the other ends are constituted by stationary plates 60c, 61c secured to the chute. As shown in Fig. 1b, rollers 55, 56 have cylindrical roller bodies 55c, 56c which are rockable by means of arms 55b, 56b which are urged by torsion coiled springs (urging mechanism) 55a, 56a so as to project into the path of feed. The can body delivering mechanism 9 has an endless chain 91 wound around a plurality of sprockets 90, L-shaped can body support members 92 which are attached top the outer side of the chain 91 at a predetermined interval so as to carry and lift the can body 8 on the can bottom anvil 8 obliquely upward, and a discharge chute 93 which receives the can body B from the can body support member 92 and delivers the can body B. The punch driving mechanism 10 includes motor 100 which is mounted on one end surface (left end surface as viewed in Figs. 4 and 6) of the stationary frame assembly 3 for rotational position adjustment, such that the axis of the motor 100 extends in the vertical direction. A pulley 101 is mounted on the output shaft of the motor 100. A fly-wheel 103 is drivingly connected to the pulley 101 through a belt 102. The fly-wheel 103 is rotatably carried through a bearing 105 by a small-diameter end of a stationary cylinder 104 attached to the frame assembly 3. An internally toothed ring gear 106 is secured to the inner surface of an intermediate portion of the stationary cylinder 104. A rotary shaft 109, the diameter of which increases in a stepped manner from a small-diameter end towards a large-diameter base end, is rotatably supported through bearings 107, 108 by the inner surfaces of the small-diameter end and the large-diameter base end of the stationary cylinder 104. A clutch brake 110 mounted on the rotary shaft 109 selectively transmits torque between the aforementioned fly-wheel 103 and the rotary shaft 109. The clutch brake 110 is so constructed as to disconnect the fly-wheel 103 from the rotary shaft 109 and to put a brake into effect when pressurized air is relieved from a pressurized air manifold 111 adjacent to the clutch brake 110. A pinion receiving portion 112 is formed in the large-diameter end of the rotary shaft 109. A hollow pinion carrier 115 is rotatably received in the pinion receiving portion 112 through the intermediary of a pair of bearings 113, 114. A pinion 116 meshing with the aforementioned ring gear 106 is carried by an intermediate portion of the pinion carrier 115. The pinion 116 has a pitch circle diameter which equals the pitch circle radius of the ring gear 106. A pitch circle extension portion 117 is formed on the base end of the pinion carrier 115 so as to extend to a position which is on the extension of the pitch circle of the pinion 116 along the axis of the latter 116. A pitch circle support shaft 118 is secured to the end of the pitch circle extension portion 117. A connecting rod 119 extending to reach the axis of the pinion 116 and, hence, the axis of the pinion carrier 115 is secured to the pitch circle support shaft 118. A connecting pin 120 is rotatably secured to the end of the connecting rod 119 reaching the axis of the pinion 116, i.e., the axis of the pinion carrier 115. The connecting pin 120 is coaxial with the pinion carrier 115, i.e., the axis of the pinion 116. To the connecting pin 120 is pivoted an end of an L-shaped rotary member 121. The L-shaped rotary member 121 has a base end which is rotatably supported by the stationary frame assembly 3 through a bearing 122. The base end of the L-shaped rotary member 121 is coaxial with the rotary shaft 109. A connecting rod 124 is rotatably carried by the above-mentioned pitch circle extension Portion 117 through a bearing 123, and a pair of sliding members 125, 126 are attached to the connecting rod 124 so as to make sliding contacts with the portion of the pitch circle extension portion 117 adjacent to the pinion carrier 115 and the pitch circle supporting shaft 118, respectively. The aforementioned punch 7 is rotatably connected at its base end to the end of the connecting rod 124 via a hollow pin 127. The aforementioned pair of punch shaft bearing mechanisms 20 include liquid bearings, i.e., hydrostatic bearings, provided on the stationary frame assembly 3. Each hydrostatic bearing has a stationary cylinder 200 and a bearing cylinder 201 received in the stationary cylinder 200. The bearing cylinder 201 is an integral member composed of a pair of annular ends 202 spaced a predetermined distance from each other and four interconnecting portions 203. The annular ends 202 and four interconnecting portions cooperate in defining four rectangular pressure ports 204. Draining grooves 205 are formed in the inner surfaces of the interconnecting portions 203. The pressure ports 204 are adapted to be supplied with a pressurized fluid from liquid supply connectors 206 which are mounted on the stationary cylinder 200. The air blow off mechanism 30 has a tube 300 which is connected at its one end to the base end of the air blow-off hole 7a of the punch 7. The other end of the tube 300 is connected to a tube mounting hole 126a which is formed in the sliding member 126 adjacent to the pitch circle support shaft 118. The tube mounting hole 126a communicates with an internal bore 118a formed in the pitch circle supporting shaft 118, via an annular space 126b which is formed in the pitch circle supporting shaft 118. The internal bore 118a has an inlet bore formed along the axis of the pitch circle supporting shaft 118 and a cross-shaped outlet bore which communicates both with the inlet bore and the annular space 126b formed in the sliding member 126. The tube 300, the tube mounting hole 126a of the connecting member 126 and the annular space 126b in cooperation form an air communication means 301 which provides a communication between the air blow-off hole 7a and the internal bore 118a of the pitch circle supporting shaft 118. A communication bore 119a formed in the connecting rod 119 communicates with the inlet bore of the internal bore 118a formed in the pitch circle supporting shaft 118. A substantially H-shaped communication bore 120b communicates with the communication bore 119a via an annular recess 120a formed in the pin 120. A substantially hook-shaped communication bore 121a, which is formed in the L-shaped rotary member 121, communicates with the communication bore 120b via an annular recess 120c formed in the connecting pin 120. The communication bore 121a is connected to a communication bore 302a formed in a ring member 302 which is attached to the L-shaped rotary member 121. The communication bore 119a, the annular recess 120a, the communication bore 120b, the annular recess 120c, the communication bore 121a and the communication bore 302a in cooperation provide an air communication passage 305. The ring member 302 is slidably mounted on a ring-shaped sliding member 303. The sliding member 303 is urged by a spring 304 on the stationary frame assembly 3 against the above-mentioned ring member 302. The arrangement is such that the communication bore 302a of the ring member 302 communicates with an air supply port 303a formed in the sliding member 303, when the above-mentioned ring member 302, i.e., the L-shaped rotary member 121, is at a predetermined angular or rotational phase. An air supply source A is connected to the air supply port 303a. The cup holder driving mechanism 40 includes a pulley 400 carried by an end of the rotary shaft 109, a pulley 403 carried by an input shaft 402a of a cam box 402 having a double cam mechanism, the pulley 403 being drivingly connected to the pulley 400 via a belt 401, a pair of tension rollers 404 for adjusting the tension of the belt 401, a pivot shaft 405 provided for a pivot motion within a predetermined angle on the output side of the cam box 402, a pair of rollers provided through connecting members 406 on both ends of the pivot shaft 405 so as to oppose each other, an inner movable cylinder 408 having roller support portions rotatably supporting the rollers 407 and movably provided on the outer periphery of the stationary cylinder 200 of the punch bearing mechanism 20 adjacent to the end of the punch 7, an outer movable cylinder 409 movably provided on the outer periphery of the inner movable cylinder 408, a pressurized chamber 410 defined between both movable cylinder 408, 409 and maintaining a predetermined internal liquid pressure therein, a pair of supporting bars 411 which are slidably supported by the roller receiving portions 408a and the supporting bar sliding portions 200a of the stationary cylinder 200, and front cylinders 412 which are connected to ends of the supporting rods 411. The aforementioned cup holder 6 is attached to the front cylinder 412. A description will be given of a process for forming a can body B by the can forming apparatus having the described construction. A cup-shaped blank C is fed into alignment with the inner bore 4a of the die 4 from the upper side of the stationary frame assembly 3, by means of the feeding mechanism 5. Then, the cup holder 6 is driven into the cup-shaped blank C by means of the cup holder driving mechanism 40, so as to locate and fix the blank C. Then, the punch 7 which is supported and guided by the pair of punch bearing mechanisms 20 is driven by the punch driving mechanism into the cup holder 6 and the bore 4a of the die 4, thereby effecting deep drawing and ironing on the can blank C, while pressing the bottom of the can blank C against the can bottom anvil 8, whereby the can body B is formed. Then, a gas, such as air, is blown by the air discharge mechanism 30 off the air blow-off hole 7a formed in the punch 7, thereby taking the can body B off the end of the punch 7. Then, the chain 91 of the can discharge mechanism 9 is actuated so that the can body B is carried by the can body supporting member 92 and is lifted obliquely upward so as to be introduced to the discharge chute 93. A detailed description will be given as to the operation of the feeding mechanism for feeding the can blank C into alignment with the inner bore 4a of the die 4. As the first step, the can blank C is held by the arcuate portions 51c, 52c of the feed guides 51, 52, as shown in Fig. 3(a). Then, the feed guides 51, 52 are rotated in counter directions as indicated by arrows in Fig. 3(b), so that the blank C supported by the arcuate portions 51c, 52c of the feed guides 51, 52 is contacted by the boundaries between the arcuate portions 51c, 52c and the recesses 51a, 52a of both feed guides 51, 52. Further rotations of the feed guides 51, 52 cause the protrusions 51b, 52b to move into the space between the blank C received in the recesses 51a, 52a and the next can blank C which rests on the first-mentioned blank C, as shown in Fig. 3(d), whereby two blanks C, C are separated from each other. Further rotations of the feed guides 51, 52 cause the recesses 51a, 52a of both feed guides 51,52 to move apart from each other as shown in Fig. 3(e), so that the blank C released from the recesses 51a, 51b is supported by the ends of the leaf springs 60b, 61b or the rollers 55c, 56c. As the feed guides 51, 52 further rotate, the protrusions 51b, 52b of the feed guides 51, 52 downwardly press the upper side of the blank C which is held on the leaf springs 60b, 61b or the rollers 55c, 56c, as shown in Fig. 3(f). Consequently, the leaf springs 60, 61 or the rollers 55c, 56c are outwardly deflected as indicated by arrows against the forces exerted by the torsion coiled springs 55a, 56a, allowing the blank C to be fed downward. As the feed guides 51, 52 further rotate, the pressing of the blank C by the protrusions 51b, 52b is terminated, so that the blank C is seated in a stationary pocket 57. Then, the feed guides 51, 52 further rotate to the positions shown in Fig. 3(a) past the positions shown in Fig. 3(h). The described operation is repeated to intermittently discharge the blank C downward. Thus, the feeding mechanism 5 separates successive can blanks C and smoothly feeds the blanks C in one-by-one fashion downward without allowing the blank C to drop freely, by virtue of the cooperation between the feed guides 51, 52 and the leaf springs 60, 61 or the rollers 55, 56. Consequently, the can blank C is softly received in the stationary pocket 57, thus avoiding collision of the can blank C with stationary parts which would inevitably lead to damage of the blanks in the conventional feeding mechanism which allows free dropping of the can blank C. Consequently, generation of noise is remarkably suppressed,and generation of defects such as dents and scratches of the can blanks C can be reduced, as compared with known feeding mechanisms. A description will now be given of the punch driving mechanism which causes reciprocating linear motion of the punch 7. Rotation of the output shaft of the motor 100 is transmitted to the fly-wheel 103 through the pulley 101 and the belt 102. In normal operation of the apparatus, the rotary shaft 109 is drivingly connected to the fly-wheel 103 through the clutch brake 110, so that the rotation of the fly-wheel 103 is transmitted to the rotary shaft 109, so that the rotary shaft 109 rotates on the bearings 113, 114. Consequently, the pinion carrier 115, which is rotatably mounted in the pinion receiving portion 112 of the rotary shaft 109 through bearings 113, 114, as well as the pinion 116 carried by the pinion carrier 115, revolves about the axis of the rotary shaft 109. As a result, the pinion 116, which is held in meshing engagement with the internal gear teeth of the ring gear 106 fixed to the stationary cylinder 104, rotates about its own axis together with the pinion carrier 115 which carries the pinion 116. As a result, the pitch circle supporting shaft 118, which is secured to the end of the pitch extension portion 117 projecting from the base end of the pinion carrier 115, makes a reciprocating linear motion with a stroke which equals to the diameter of the pitch circle of the ring gear 106, together with the connecting rod 124 which is rotatably connected to the pitch circle supporting shaft 118 through the bearing 123 and also together with the hollow pin 127 and the punch 7. In Figs. 4 and 9, the pitch circle supporting shaft 118 is positioned at the left end of the pitch circle of the ring gear 106. Thus, the pitch circle supporting shaft moves reciprocatingly and linearly between this position and the right end of the pitch circle of the ring gear 106. A description will be given of the relationships between the ring gear 106, the pinion 116 meshing with the internal teeth of the ring gear 106 and the pitch circle supporting shaft 118 secured to the end of the pitch circle extension 117, with specific reference to Figs. 14 to 17. The pinion 116 has a pitch circle diameter which equals to the pitch circle radius of the ring gear 106. Therefore, a point P on the pitch circle of the pinion 116 (point on the axis of the pitch circle supporting shaft 118) moves along the pitch circle diametrical line D from the left end to the right end and then moved back from the right end to the left end of the diametrical line D as viewed in Figs. 14 to 17, thus making a reciprocating linear motion, as the pinion 116 revolves along the inner periphery of the ring gear 106 while rotating around its own axis, i.e., as the pinion 116 revolves from the position shown in Fig. 14 to the position shown in Fig. 17 past the positions shown in Figs. 15 and 16 and further back to the position shown in Fig. 14. The point P on the pitch circle of the pinion 116 also makes one rotation while making one full reciprocating linear motion, i.e., during the period in which it make one full revolution along the inner periphery of the ring gear 106. Consequently, the pitch circle supporting shaft 118 also rotates about its own axis while making one full reciprocating linear motion. Referring to Fig. 9, as a result of the rotation of the pitch circle supporting shaft 118, the connecting rod 124 which is rotatably connected to the pitch circle supporting shaft 118 through the bearing 123 makes reciprocating linear motion while allowing smooth rotation of the pitch circle supporting shaft 118 through the bearing 123, so that the punch 7 which is connected to the connecting rod 124 through the hollow pin 127 quickly moves reciprocatingly and linearly without making any oscillation in the direction transverse to the axis thereof. It is therefore possible to smoothly insert the punch 7 into the die bore 4a of the die 4, thus enabling a high-speed production of the can body B. Meanwhile, the end of the connecting rod 119 attached to the pitch circle supporting shaft 118, reaching the axis of the pinion 116, i.e., the axis of the pinion carrier 115, revolves together with the connecting pin 120 rotatably connected to the end thereof around the axis of the ring gear 106, i.e., the axis of the rotary shaft 109, as is the case of the axis of the pinion 116. In addition, the L-shaped rotary member 121 which rotatably supports the connecting pin 120 revolves about the axis of the ring gear 106, i.e., the axis of the rotary shaft 109, in accordance with the revolution of the connecting pin 120. As explained before, during the reciprocating linear motion of the punch 7, a pressurized liquid is supplied into four rectangular pressure ports 204 from four liquid supply connectors 206 through the stationary cylinders 200 of the punch bearing mechanisms 20. The pressurized liquid thus supplied keeps the punch 7 floated apart from the inner surface of the bearing sleeve 201, thereby remarkably reducing friction between the punch and the bearing sleeve 201 while smoothly guiding the reciprocating linear motion of the punch 7. The rotation of the rotary shaft 109 is transmitted to the input shaft 402a through the pulley 400, belt 401 and the pulley 403 of the aforementioned cup holder driving mechanism 40, so that the rollers 407 on two connecting members 406 rock within a predetermined angular range about a pivot shaft 405. The rocking motion of the rollers 407 causes, through roller holders 408a holding these rollers 407, the inner movable cylinder to slide back and forth along the stationary cylinder 200 of the punch bearing mechanism 20. This sliding motion causes, through the pressurized chamber 410, the outer movable cylinder 409 to move in the same direction as the movement of the inner movable cylinder 408, so that a pair of supporting rods 41 secured to the outer movable cylinder 409 make sliding motion while being supported by the roller holders 408a and the supporting rod sliding portions 200a of the stationary cylinders 200. The sliding movement of the supporting rods 411 causes, through the front cylinders 412 secured to the ends of these rods 411, the cup holder 6 to move towards and away from the die 4. Consequently, the cup holder 6 is inserted into the blank C set in the bore 4a of the die 4 so that the cup-shaped blank C is clamped, located and fixed between the cup holder 6 and the die 4, to prepare for the deep drawing and ironing to be effected on the blank C set in the bore 4a of the die 4. The arrangement is such that the rollers 407 on the upper ends of the pair of connecting members 406 which rock about the pivot shaft 405, as well as the inner movable cylinder 408 connected through the roller holders 408a holding the rollers 407, are positioned slightly ahead of the positions corresponding to the forward stroke end of the cup holder 6, i.e., so as to project slightly beyond these positions towards the die 4, when the cup-shaped blank C is held between the cup holder 6 and the die 4. In operation, however, the forward movement of the cup holder 6 is blocked by the cup-shaped blank C, so that the front cylinder 412 which directly drives the cup holder 6, as well as the supporting rods 411 and the outer movable cylinder 409, is retracted relative to the inner movable cylinder 408 against the resilient pressing force generated by the pressurized chamber 410. Thus, the cup holder 6 firmly presses the blank C against the die 4 by the pressing force generated by the pressurized chamber 4, whereby the blank C is stably held in the right position. If the cup-shaped blank C has not been correctly set in the right position inside the bore 4a of the die 4, an abnormally large pressing force is exerted on the cup holder 6 when the cup holder is brought into contact with the blank C. This causes an abnormal pressure rise in the pressurized chamber 410. In such a case, the pressure inside the pressurized chamber 410 is relieved so as to allow the cup holder 6, front cylinder 412, supporting rods 411 and the outer movable cylinder 409 to be retracted relative to the inner movable cylinder 408, thereby preventing break down or damaging of the cup holder 6 and tools including the die 4. The can body B is formed in the described manner by the cooperation between the punch 7 and the die bore 4a and the can bottom anvil 8 of the die. The can body B is then taken off the punch 7. To this end, the communication hole 302a in the ring member 302 attached to the L-shaped rotary member 121 is brought into communication with the air supply hole 303a formed in the sliding member 303 which is held in sliding contact with the ring member 302 by the force of the spring 304. Consequently, a gas such as air is introduced from the air supply source A into the air blow-off hole 7a formed in the punch 7, through the air supply port 303a, communication hole 302a, communication hole 121a in the L-shaped rotary member 121, annular recess 120c,communication hole 120b and the annular recess 120a of the connecting pin 120, communication hole 119a in the connecting rod 119, internal bore 118a of the pitch circle supporting shaft 118, annular recess 126b of the sliding member 126, tube mounting hole 126a and the tube 300. Consequently, the gas such as air is discharged from the end of the air blow-off hole 7a, so that the can body B can easily be separated and taken from the punch 7. Meanwhile, the sliding member is held securely in pressure contact with the ring member 302 by the force exerted by the spring 304, and a tight seal is formed between the connecting pin 120 and adjacent members including the L-shaped rotary member 121 and the connecting rod 119, as well as between the pitch circle supporting shaft 118 and the sliding member 126, so that the gas such as air from the air supply source A does not leak before reaching the air blow-off hole 7a, despite the motions of the individual members such as the ring member 302 and the L-shaped rotary member 121, connecting pin 120, connecting rod 119, pitch circle supporting shaft 118 and the sliding member 126. It is therefore possible to discharge the air from the end of the air blow-off hole 7a of the punch 7 at a proper timing. The tube 300 is used to provide communication only between the sliding member 126 and the punch 7 which perform synchronized reciprocating linear motion, so that the tube 300 does not come off nor be damaged despite the high-speed motion of the punch 7, thus ensuring stable operation of the apparatus for a long period of time. Operation: The blank introduced into the path of feed is temporarily stopped upon contact with the outer peripheral surfaces of the feed guides. As the feed guides are rotated, the blank is then embraced and fed downward by the recesses formed on the peripheries of the feed guides. The can blank fed downward is then stopped by the pair of leaf springs or rollers. However, as the feed guides are further rotated, the protrusions on the peripheries of the feed guides press the can blank downward against the leaf springs or the rollers, so that the leaf springs or rollers are forced out of the path of feed against the urging force exerted by the urging means. The blank thus fed is set into the die bore of the die by means of the punch which is driven by the punch driving mechanism and supported and guided by the punch bearing mechanism, so that deep drawing and ironing are effected on the can blank to form it into a can body. Then, a gas is discharged by the gas discharging mechanism from the gas blow-off hole formed in the center of the punch, whereby the can body is separated from the end of the die. The pinion having a pitch circle diameter equal to the pitch circle radius of the ring gear is made to revolve about the axis of the ring gear along the inner periphery of the ring gear in meshing engagement with the internal gear teeth of the ring gear. Consequently, the pinion makes a rotation about its own axis so that a predetermined point on the pitch circle of the pinion reciprocatingly and linearly move along a diametrical line of the ring gear, whereby the punch which is rotatably held on the above-mentioned point makes reciprocating linear motion. The punch is guided by the fluid bearing during the reciprocating linear motion thereof so that fluid pressure exists between the punch and the punch supporting portion to prevent direct contact therebetween. Further, gas supplying means provided on a stationary part of the apparatus may supply a gas into the gas blow-off hole of the punch after completion of the deep drawing and ironing, thereby separating the can body from the end of the punch. The gas supplying means provided on the stationary part of the apparatus supplies a gas to the gas communication passage in the rotary member at a predetermined rotational angular phase of the rotary member, the gas being then supplied through the gas communication passage and via the axis of the pinion to the interior of the support shaft provided on the pitch circle of the pinion. The gas then further flows through the gas flow means to the gas blow-off hole in the punch so as to be discharged therefrom, thereby separating the can body from the end of the punch. Explanation of Numerals and Symbols: A: gas supplying source (gas supplying means) B: can body C: blank 4: die 4a: die bore 5: feeding mechanism 7: punch 7a: gas blow-off hole 10: punch driving mechanism 20: punch bearing mechanism 30: gas discharging mechanism 50: chute 51, 52: feed guide 51a, 52a: recess 51b, 52b: protrusion 55, 56: roller 55a, 56a: torsion coiled spring (urging means) 55c, 56c: rollers 60, 61: leaf spring 60a, 61a: leaf spring member 60b, 61b: end of leaf spring 60c, 61c: fixed plate 100: motor (pinion driving mechanism) 106: ring gear 109: rotary shaft (pinion driving mechanism) 116: pinion 118: pitch circle supporting shaft 121: L-shaped rotary member 301: gas flow means 303: sliding member 305: gas communication passage

Claims: A can forming apparatus of the type in which a punch (7) is reciprocatingly and linearly moved into and out of a die bore (4a) in a die (4) so as to effect deep drawing and ironing on a blank (C) to form said blank into a can body (B), said can forming apparatus comprising: an internally toothed ring gear (106), a pinion (116) having a pitch circle diameter equal to the pitch circle radius of said ring gear (106) and adapted to revolve along the inner periphery of said ring gear (106) in meshing engagement with the internal teeth of said ring gear (106), a pinion driving mechanism (100) connected to said pinion (116) to cause said pinion (116) to revolve around the axis of said ring gear (106), a punch supporting means (118) for rotatably supporting said punch (7) on the pitch circle of said pinion (116), a gas blow-off hole (7a) formed in said punch (7) to blow a gas off the center of said punch (7), characterized in that the can forming apparatus further comprises: a gas flow means (301) providing a communication between said gas blow-off hole (7a) formed in said punch (7) and the interior of a support shaft provided on the pitch circle of said pinion (116) rotatably supporting said punch (7), a gas communication passage (305) providing a communication between said interior of said support shaft and a rotary member which rotates about the axis of said ring gear (106), via said axis of said pinion (116), and a gas supplying means provided on the stationary parts of said apparatus and held in sliding contact with said gas communication passage (305) of said rotary member so as to supply the gas into said gas communication passage (305) at a predetermined angle of rotation. A can forming apparatus according to claim 1, wherein said punch (7) is movably supported by a shaft supporting portion including a fluid bearing.

Inventors: AKIRA KAWAGUCHIC, TOSHIHIKO KAWASHIMAC, AKIRA KAWAGUCHI, TOSHIHIKO KAWASHIMA, Akira Kawaguchic/o Ikuno Plant Mitsubishi corp., Toshihiko Kawashimac/o Aluminum Can Devpl Center
Applicants: MITSUBISHI MATERIALS CORP, MITSUBISHI MATERIALS CORPORATION
Application year: 1993
Main classification: B21D51
IPC codes: B21D45, B21D43, B21D51, B21D22