CA1159314A - Double action press having floating punch - Google Patents
Double action press having floating punchInfo
- Publication number
- CA1159314A CA1159314A CA000376029A CA376029A CA1159314A CA 1159314 A CA1159314 A CA 1159314A CA 000376029 A CA000376029 A CA 000376029A CA 376029 A CA376029 A CA 376029A CA 1159314 A CA1159314 A CA 1159314A
- Authority
- CA
- Canada
- Prior art keywords
- punch
- slide
- blanking
- press
- forming
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
- B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
- B21D24/14—Devices controlling or operating blank holders independently, or in conjunction with dies pneumatically or hydraulically
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D35/00—Combined processes according to or processes combined with methods covered by groups B21D1/00 - B21D31/00
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
- Presses And Accessory Devices Thereof (AREA)
- Shaping Metal By Deep-Drawing, Or The Like (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A double action mechanical press, especially for performing a blanking operation and a forming operation on each cycle thereof, having a first slide and a second slide, wherein the slides have separate strokes. The slides are reciprocated by means of a crankshaft and connecting rod assembly comprising a single crankshaft and a plurality of connecting rods wherein the throws of the crankshaft can be differ-ently dimensioned and angularly offset relative to each other so as to provide different stroke lengths for the slides and to cause one slide to lead the other. A guide bushing assembly is connected to one of the press slides, and a blanking punch is received in the guide bushing for reciprocating movement relative to the bushing along the same direction of reciprocating movement as the slides. A preloaded antifriction bearing is positioned between the punch and bushing assembly, and serves to maintain the proper clearance between the punch and the corresponding cutting edge on the lower die half. A forming die is received in the guide bushing assembly for reciprocating movement relative thereto and is connected to the other press slide. The other portion of the punch is formed as a piston and is urged downwardly by pressurized air. The travel of the punch against the pressurized air enables the punch to abut the top of the strip material until the blanking slide strikes it and causes it to blank out the part. Meanwhile, the forming die draws the blanked out part, which is continued to be held by the pressure of the punch against the liftout ring. Thus, the action of the floating punch simulates the dwell provided by a cam driven punch.
A double action mechanical press, especially for performing a blanking operation and a forming operation on each cycle thereof, having a first slide and a second slide, wherein the slides have separate strokes. The slides are reciprocated by means of a crankshaft and connecting rod assembly comprising a single crankshaft and a plurality of connecting rods wherein the throws of the crankshaft can be differ-ently dimensioned and angularly offset relative to each other so as to provide different stroke lengths for the slides and to cause one slide to lead the other. A guide bushing assembly is connected to one of the press slides, and a blanking punch is received in the guide bushing for reciprocating movement relative to the bushing along the same direction of reciprocating movement as the slides. A preloaded antifriction bearing is positioned between the punch and bushing assembly, and serves to maintain the proper clearance between the punch and the corresponding cutting edge on the lower die half. A forming die is received in the guide bushing assembly for reciprocating movement relative thereto and is connected to the other press slide. The other portion of the punch is formed as a piston and is urged downwardly by pressurized air. The travel of the punch against the pressurized air enables the punch to abut the top of the strip material until the blanking slide strikes it and causes it to blank out the part. Meanwhile, the forming die draws the blanked out part, which is continued to be held by the pressure of the punch against the liftout ring. Thus, the action of the floating punch simulates the dwell provided by a cam driven punch.
Description
DOU~I.E' ACTIO~I PRF~S HAV NG
FLOATI~G PUNCH
The present invention relates to mechanical presses, and in ~ar~icular to double action presses wherein a blanking and forming operation is performed on each cycle o the press.
In ma~ing can ends, ~or example, one slide of the press performs the blanking operation, which punches out a circular blank from strip stock, and the other slide forms the circular blank into a can end by means of a drawing o~eration. rrhus, both operations can be performed on a single cycle of the press.
Due to the fact that the blanking operation must be carried out prior to the drawing operation, pres~es of this type are constructed such that the blanking slide will lead the forming slide. Furthermore, it is necessary t~ hold the blanked part during at least a portion of the drawing op~ration so as to prevent wrinkling. Some prior art presses have accomp-lished ~his by permitting the blan}cin~ punch to travel through the tin line and con-tinue to exert pressure on the blanked part during the drawincJ operation~
By permitting the hlanking punch to overtravel past the cutting edge, excess$ve wear of the cutting edge is cau~ed h~ the punch sliding ~ast it. Unless proper clearance between -the punch and cutting edge can be maintained at all times, metal to metal contact betwean the punch and cutting edge will occur during the o~ertravel portion of the cycle. ~ urther di~advan tage to overkr~v~l of the hlanking puncll ~s that the punch will nece~arily have a longe~ re~dence time beneath the tin line th~n will the eormLng die, ancl thi~ d~lay~ e~ctlon o~ the einishe~1 part.
In o~cler to avoicl overtravel Oe the blanlcin~
punch, certaLn t~pes of presses ~r:Lve the blankin~
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unch slide by means of a cam. The cam is manufactured so tha-t the blanking punch is caused to dwell a-t the bottom of its stroke at a point ~ust below the tin line. This maintains pressure on the blanked part yet avoids overtravel so that the blanking punch can begin its re-turn stroke at the same time as or just before the return stroke of the forming die. In a cam driven press of this type, the mechanism is quite complicated. Moreover, the fact that the contact between the cam and connectïn~ rod is only a line contact, lubrication is difficult and the cam surEaces are subject to wear.
According to the present invention there is provided a double action press which has a bed portion, a blanking slide, a forming slide with drive means connected to the slides for reciprocating the slides along respective rectilinear pathsl the drive means including a crankshaft having at least two eccentrics thereon and at least two connecting rods connecting respective slides and respective eccentrics, the drive means causing the blanking slide to lead the forming slide. A forming die is provided which includes a first forming tool element connected to the forming slide and a second forming tool element connected to the bed portion of the press, the tool elements being adapted to coact with each other to form a part therebetween when brought together by the forming slide. A blanking die is provided which includes a blanking punch connected to the blanking slide and a blanking tool element connected to the bed portion o~ the press, the punch and blanking tool element being adapted to coact with each other to cut out a blank when brought together by the blanking slide at about the dead center position of the eccentric driving the blanking slide. The punch is reciprocally connected to the blanking slide for movement relative to the blanking slide in a direction parallel to the rectilinear movement o~ -the blanking slide. The drive means causes the blanking slide to positively ancl non-yieldably enga~e khe punch about the dead center po~ition of the eccen-tric driving the blanking slide to cu-t ou-t a blank. Means yieldably urges thq punch in the rectilinear direc-tion oE
-kh~. blanking slide away Erom the blanking ~lide to elx-tend B pc~b . ... . . ..
.
3~4 elative to -the blanking slide and exert a holding force on the blank as a blanking slide moves away.
The above problems and disadvantages of prior art double action presses utilized for a blanking and forrning operation are overcome by driving the two slides by means of the crankshaft and connecting rod assembly, yet simulates the dwell achieved by prior art cam driven presses. The blanking and drawing slides are driven ~y means of a cranksha~t and connecting rod assembly such as that disclosed in U.S. Letters Patent 3,902,347, which is owned by the assignee of the present application. It has been found that this type of press drive results in a relatively simple, but extremely rigid structure. Since the'connecting rods surround the crankshaft throws, a much larger oil film results, thereby reducing wear between these parts.
I'he dwell produced by prior art cam drives is simulated by permitting the blanking punch to float within the guide bushing structure connected to the blanking slide.
The punch is received within the bushing assembly for reciprocating movement relative to -the blanking slide along, the same rectilinear direction of movement as the slide. The upper portion of the blanking punch may be formed as a piston and reciprocates within a cylinder formed in the bushing assembly. Pressurized air may be admitted to the cylinder and continuously urges the punch downwardly. On the downstroke of the blanking slide, the punch initially contacts the strip of material, but does not cut through the materia,l until the blanking slide catches up with it and drives the punch through the material to cut the blank. The pressurized air maintains the punch in clamping engagement with the blanked part during at least a portion of the drawing operation, and the blanking slide will li~t the punch at the same time as the forming die is lifted by its slide. Since the blanking punch and ~ormin~ dic are li~ted togq-ther, the part can be ejected mu~h more quicl~ly than if khe punch over-traveled as in the case oE c~rtain prior ar-t p~esses.
~ Eurther advankage to main-tainlng contac-k between the blan~ing punch and park i9 tha-t i~ facilitates stripping the park ~rom the lower die. rrhe closer khe punch is to ~0 the drawing die when the par-t is s-tripped, t.he more control pc/t~
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-:an be maintained on the par-t during -the stripping and ejecting sequence.
A significant problem with floating punches per se is that of maintaining alignment and proper clearance relative to the cutting edge, especially with thin stock.
If proper clearance is not maintained, the punch may contact the cutting edge during the blanking stroke, thereby chipping the cutting edge. The punch assembly according to an embodiment of the present invention overcomes this problem by providing preloaded antifriction bearings between the punch and the guide bushing, which very accurately guide and align the punch. as it reciprocates within the guide bushing assembly and as it is reciprocated by the bIanking slide itself.
It is an object of the present invention to provide a double action press wherein blanking.and forming operations can be performed in a single cycle of the press, and wherein overtravel of the blanking punch is avoided.
It is a further object of the present invention ~0 to provide a double action press wherein the dwell of a blanking punch is accomplished without resorting to the use of a cam drive. This object is accomplished by utilizing a crankshaft drive for the slides, wherein the blanking punch is permitted to reciprocate relative to the blanking slide against the pressure of a yieldable medium.
These and other objects and features of the present invention will become apparent from the description .
of the preferred embodiment, taken together with the drawings~
Figure 1 is a front elevational view of a press .incorporating the present invention;
Figure 2 is an enlarged, fragmentary, sectional view of the press illustrating the blanking and forming punch assembly wherein the blanking slide has moved to the 140 position of its cycle;
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Figure 3 is a view similar to Figure 2 wherein the blanking slide i5 at bottom clead center or 180 of its cvcle;
Figure 4 is a view sirnilax to Figures 2 and 3 wh~rein the blanking slide is at 254 of its cycle;
Figure 5 is an enlaryed, sectional view o the liftout mechanism;
Figure 6 is a yraph plo~ing the postions oE
the blanking slide, forming slicle and punch above bo~tom dead center and abov~ he strip stoc}c for a complete press cycle; and Figure 7 is a diagrammatic view o:f the drive mechanism ~or the lides.
Referring now to the drawings in detail, E'igure 1 illustrates a press 10 comprising a crown 12 connected to a hed 14, the latter beinc3 sup~orted on legs 16.
The press crankshaft 1~ is driven by an electric motor 20 connected ~hereto by a belt and pu112y m~chanism and a clutch (not shown3. Figure 7 illustrates diagram-matically the connec~ions between crankshaEt 18 and connecting rods 20, which are connected to the blanking slide 21 (Figure 1), and connecting rod 22, which is connected to the forming slid~ 24 (Figure 1).
Outermost eccenkrics 25 are pivotall~ connectecl to blanking slide connecting rods 20, and innermost crankpin 28 is pivotally connected to formincJ ~lide connecting rod 22. Crankpin 28 i5 angularly o~fset with respect to eccentrics 26 so that connecting rods 20 and blanking ~lide 21 will lead connecting rod 22 and ~orming slide 24 as crankshat 18 turns.
Fur-th~rmore, crankpin 28 i.s ~uch -that the total rectilin-ear tra~el o~ connect:LncJ rod 22 and ~orming 31id~
FLOATI~G PUNCH
The present invention relates to mechanical presses, and in ~ar~icular to double action presses wherein a blanking and forming operation is performed on each cycle o the press.
In ma~ing can ends, ~or example, one slide of the press performs the blanking operation, which punches out a circular blank from strip stock, and the other slide forms the circular blank into a can end by means of a drawing o~eration. rrhus, both operations can be performed on a single cycle of the press.
Due to the fact that the blanking operation must be carried out prior to the drawing operation, pres~es of this type are constructed such that the blanking slide will lead the forming slide. Furthermore, it is necessary t~ hold the blanked part during at least a portion of the drawing op~ration so as to prevent wrinkling. Some prior art presses have accomp-lished ~his by permitting the blan}cin~ punch to travel through the tin line and con-tinue to exert pressure on the blanked part during the drawincJ operation~
By permitting the hlanking punch to overtravel past the cutting edge, excess$ve wear of the cutting edge is cau~ed h~ the punch sliding ~ast it. Unless proper clearance between -the punch and cutting edge can be maintained at all times, metal to metal contact betwean the punch and cutting edge will occur during the o~ertravel portion of the cycle. ~ urther di~advan tage to overkr~v~l of the hlanking puncll ~s that the punch will nece~arily have a longe~ re~dence time beneath the tin line th~n will the eormLng die, ancl thi~ d~lay~ e~ctlon o~ the einishe~1 part.
In o~cler to avoicl overtravel Oe the blanlcin~
punch, certaLn t~pes of presses ~r:Lve the blankin~
~LS~3~19L
unch slide by means of a cam. The cam is manufactured so tha-t the blanking punch is caused to dwell a-t the bottom of its stroke at a point ~ust below the tin line. This maintains pressure on the blanked part yet avoids overtravel so that the blanking punch can begin its re-turn stroke at the same time as or just before the return stroke of the forming die. In a cam driven press of this type, the mechanism is quite complicated. Moreover, the fact that the contact between the cam and connectïn~ rod is only a line contact, lubrication is difficult and the cam surEaces are subject to wear.
According to the present invention there is provided a double action press which has a bed portion, a blanking slide, a forming slide with drive means connected to the slides for reciprocating the slides along respective rectilinear pathsl the drive means including a crankshaft having at least two eccentrics thereon and at least two connecting rods connecting respective slides and respective eccentrics, the drive means causing the blanking slide to lead the forming slide. A forming die is provided which includes a first forming tool element connected to the forming slide and a second forming tool element connected to the bed portion of the press, the tool elements being adapted to coact with each other to form a part therebetween when brought together by the forming slide. A blanking die is provided which includes a blanking punch connected to the blanking slide and a blanking tool element connected to the bed portion o~ the press, the punch and blanking tool element being adapted to coact with each other to cut out a blank when brought together by the blanking slide at about the dead center position of the eccentric driving the blanking slide. The punch is reciprocally connected to the blanking slide for movement relative to the blanking slide in a direction parallel to the rectilinear movement o~ -the blanking slide. The drive means causes the blanking slide to positively ancl non-yieldably enga~e khe punch about the dead center po~ition of the eccen-tric driving the blanking slide to cu-t ou-t a blank. Means yieldably urges thq punch in the rectilinear direc-tion oE
-kh~. blanking slide away Erom the blanking ~lide to elx-tend B pc~b . ... . . ..
.
3~4 elative to -the blanking slide and exert a holding force on the blank as a blanking slide moves away.
The above problems and disadvantages of prior art double action presses utilized for a blanking and forrning operation are overcome by driving the two slides by means of the crankshaft and connecting rod assembly, yet simulates the dwell achieved by prior art cam driven presses. The blanking and drawing slides are driven ~y means of a cranksha~t and connecting rod assembly such as that disclosed in U.S. Letters Patent 3,902,347, which is owned by the assignee of the present application. It has been found that this type of press drive results in a relatively simple, but extremely rigid structure. Since the'connecting rods surround the crankshaft throws, a much larger oil film results, thereby reducing wear between these parts.
I'he dwell produced by prior art cam drives is simulated by permitting the blanking punch to float within the guide bushing structure connected to the blanking slide.
The punch is received within the bushing assembly for reciprocating movement relative to -the blanking slide along, the same rectilinear direction of movement as the slide. The upper portion of the blanking punch may be formed as a piston and reciprocates within a cylinder formed in the bushing assembly. Pressurized air may be admitted to the cylinder and continuously urges the punch downwardly. On the downstroke of the blanking slide, the punch initially contacts the strip of material, but does not cut through the materia,l until the blanking slide catches up with it and drives the punch through the material to cut the blank. The pressurized air maintains the punch in clamping engagement with the blanked part during at least a portion of the drawing operation, and the blanking slide will li~t the punch at the same time as the forming die is lifted by its slide. Since the blanking punch and ~ormin~ dic are li~ted togq-ther, the part can be ejected mu~h more quicl~ly than if khe punch over-traveled as in the case oE c~rtain prior ar-t p~esses.
~ Eurther advankage to main-tainlng contac-k between the blan~ing punch and park i9 tha-t i~ facilitates stripping the park ~rom the lower die. rrhe closer khe punch is to ~0 the drawing die when the par-t is s-tripped, t.he more control pc/t~
. . ' ' ':
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-:an be maintained on the par-t during -the stripping and ejecting sequence.
A significant problem with floating punches per se is that of maintaining alignment and proper clearance relative to the cutting edge, especially with thin stock.
If proper clearance is not maintained, the punch may contact the cutting edge during the blanking stroke, thereby chipping the cutting edge. The punch assembly according to an embodiment of the present invention overcomes this problem by providing preloaded antifriction bearings between the punch and the guide bushing, which very accurately guide and align the punch. as it reciprocates within the guide bushing assembly and as it is reciprocated by the bIanking slide itself.
It is an object of the present invention to provide a double action press wherein blanking.and forming operations can be performed in a single cycle of the press, and wherein overtravel of the blanking punch is avoided.
It is a further object of the present invention ~0 to provide a double action press wherein the dwell of a blanking punch is accomplished without resorting to the use of a cam drive. This object is accomplished by utilizing a crankshaft drive for the slides, wherein the blanking punch is permitted to reciprocate relative to the blanking slide against the pressure of a yieldable medium.
These and other objects and features of the present invention will become apparent from the description .
of the preferred embodiment, taken together with the drawings~
Figure 1 is a front elevational view of a press .incorporating the present invention;
Figure 2 is an enlarged, fragmentary, sectional view of the press illustrating the blanking and forming punch assembly wherein the blanking slide has moved to the 140 position of its cycle;
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Figure 3 is a view similar to Figure 2 wherein the blanking slide i5 at bottom clead center or 180 of its cvcle;
Figure 4 is a view sirnilax to Figures 2 and 3 wh~rein the blanking slide is at 254 of its cycle;
Figure 5 is an enlaryed, sectional view o the liftout mechanism;
Figure 6 is a yraph plo~ing the postions oE
the blanking slide, forming slicle and punch above bo~tom dead center and abov~ he strip stoc}c for a complete press cycle; and Figure 7 is a diagrammatic view o:f the drive mechanism ~or the lides.
Referring now to the drawings in detail, E'igure 1 illustrates a press 10 comprising a crown 12 connected to a hed 14, the latter beinc3 sup~orted on legs 16.
The press crankshaft 1~ is driven by an electric motor 20 connected ~hereto by a belt and pu112y m~chanism and a clutch (not shown3. Figure 7 illustrates diagram-matically the connec~ions between crankshaEt 18 and connecting rods 20, which are connected to the blanking slide 21 (Figure 1), and connecting rod 22, which is connected to the forming slid~ 24 (Figure 1).
Outermost eccenkrics 25 are pivotall~ connectecl to blanking slide connecting rods 20, and innermost crankpin 28 is pivotally connected to formincJ ~lide connecting rod 22. Crankpin 28 i5 angularly o~fset with respect to eccentrics 26 so that connecting rods 20 and blanking ~lide 21 will lead connecting rod 22 and ~orming slide 24 as crankshat 18 turns.
Fur-th~rmore, crankpin 28 i.s ~uch -that the total rectilin-ear tra~el o~ connect:LncJ rod 22 and ~orming 31id~
2~ is gr~atex than the total r~ctilinear trav~l Oe blanking conneatin~ rod~3 20 and ~31id~ 21. Th~ relative movem~nt~ Oe blanking ~ 21 and ~orming slide 2~ are Lllustra~d in ~.lgure 6. ~'he ~iqn o~ crank3ha~
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18 to accomplish this rela~ive movement is within normal engineering expertise.
The shell ty~e bearincJ slaeves 30 are preerably pressure lubricated through pas~ages 32 connected s to a lubricant suppl~ (not shown).
Strip stock is fed into prPss 10 by fe2d 36, and the scrap is cut off by means o~ scrap cutter 38. A liftout mechanism 40 is clriven by means o chain, ~elt, or other power transmission 42, whicll is connected to sprocket 4 4 and to sprocket 43, the latter driv2n by cxanksha~t 18.
Re~erring now to Fi~ures 2, 3 and 4, ~he de~ails of the punch assembly will be described~ Bolst~r 46 is secured to bed 14 and lowex liftout pin retainer 1~ plate 48 is supported on the upper sllr~ace 4~ thereof.
Draw ring retainer 50 is supported on liftout pin retainer ~8, and serves to retain draw ring 52 in position. It will be noted that draw ring 52 includes an annular upstanding portion 54 around which cuttlng die retainer 56 is posi~ioned. Cutting die retainer 56 is secured to draw ring re~ainer 50, and includes an annular step 60 within which annular cutting die 58 is received. Cutting die 58 inclucles a cutting edge 62, which cooperates with ~he edga ~4 o~ ptmch 66 to stamp out a circular blank when p~nch 66 i~
driven downwardly past cutting edge 62, as wlll be described below. Filler plate 6n overlies and ls secur~d to die retainer plate 56, and the upper sur~ace 70 thereof supports the strip stock 240 as it is advanced through the press in a hoxizontal directionO
Cover plate 72 is rigidly sQcured in posltion/ and -~he lowe~ sur~ace 74 thereoe 1~ s~aced ro~ the upper ~r~ace 70 o~ r plate 68 ~o as to p~ovide a ,qubstantiall~ planar ~hannel ~hrou~h wlllch ~e ~toc]c material i~ ~d. The s~aae between ~ureac~ 70 and 74 generally de~ine~ what is known in the lnclu~try .
~L ~ o~314~
as the tin linel a hori~ontal o:r inclined plane -through which the strip stock is fed hy feed mechanism 36 (Fi~ure 1).
Lower forming die 76, the cross section of which S is circular in a plane parallel to th~ tin line, is connected to draw rinc3 52 by screws 78. Thus, draw ring retainer 50, clraw ring 52, lower formin~ :
die 76, pin retainer plate 48 and bolst~r 46 are rigidly connected to the press frame. ~ower forming dia 76 includes an annular bea~ portioll 80, which forms a corr~spondingly shaped bead 82 in the finished can end 84 illustrated in Figure 4~
Liftout element 86, which includes a generally circular base 88 and an upstanding annular rim portion 90, is sliclably received within draw ring 52 ~or reciprocating movement in the same direction as ~hs direction of movement of s1ides 21 and 24. Liftout member S8 is yieldably pulled downwardly by mean~
of liftout stem 92, which is threadedly secured to the base portion 88, and compression spring 94, which is disposed between the lower surfac2 96 of pin retainer plate 48 and a washer lQ0 held in place hy nut 102.
The holding force developeel by spring 94 can be adjusted by means of nut 102. ~i~tout member 86 slides around the lower portion 104 o~ lower forming die 76, and when retracted, its lower sur~ac~ 108 is in abutment with the upper surface l.L0 o~ draw rlng S2.
Li~tout member 36 is pushe~ to its lntermediate position by means o~ liEtout pins 112, which are .~0 slidably received in bushings 114 retained within pin retainer plate 4~ ietout pin~ :L12 are ~ressed upwardl!y h~ stems 116, which are ~onnected to piskolls (not shown~ wikhin pressur~ a~linders L18, the latter bf3~n~ khreadedly ~ecured to bolst~r 46 an~l seal~d 3S th~3rea(3a~llst b~ 0-~rin~s 120.A eluic1 passa(3e 1~2 ., ~ :
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is connected to a source of pressurized air to yieldably lift the blanked part against the actic)n of uppar die 170. It will be noted that the upper end of pin 112 engages the lower surface 10~ of liftout member 86 so as to raiYe liftout member 86 against the action of spring 94. Stem 92 is lifted by plate 124, which slides over screws 126 connected to bolster 46. Figure 3 illustrates plata 124 in its Eully retracted po~ition.
Turning now to the upper portion of the die set, a housing assembly 128 is slidably disposed with respect to spindle 130, and retains punch 66 fox slidable movement relative thereto. ~ou~ing a~sembly 12~ comprices a ~pindle alignment bearing 132 connected to slicle 21 by scraws 134, and a guide bushing 136 connected to spin~le alignment bearing by screws 138. The upper por-tion of punch 66 i~
for~ed as an annular piston 140 including seals 141 and 142, and reciprocat~s within an annular cylinder 144 defined by spindle alignment bearing 132 and an annular step in guide bushing 136. The intermediate portion 146 of punch 66 i~ annular and cylindrical in shape, and punch 66 includes a tapered transition portion 148 between intermediate portion 146 and the lower cutting portion 150 including cutting edge 64. Air pressure from passage 149 yiQldably and continuously urges punch 66 downwardly to the positlon o~ Figure 4.
Punch 66 i~ very accurately guided and aligned within guide bushing 136 by means of cylindrical ~all bearing as~embly 152, which comprise~ a cylindrical rat~iner h~ving a plurallty o~ ball b~aring~ 154 aaptu~cl therein. ~ portion of the hall bearings 1$4 ~x~ ln roll:lng enga~amant with the out~r cylindrical 3r~ ~ur~ace 156 o:E the in~ermediate p~r-tlon 146 o~ punch ' , ~ ;" ' ' ~''3~ 31~
66, and the remainder of the ball bearin~s 154 are in rolling engagement with the inner concave cylindrical sur~ace 153 of guide bushin~ 136. Bearing assembly 152 is held in place by bearing re~ainer 160, which 5 is secured to guide hushing 136 b~ screws 162. Bear-ing assembly 15~ is prPferably preloaded so that very precise tolerances can be maintained with respect to the position oE the punch 66 relative to cutting ; edge 62. As discussed above, this is important from the standpoint o~ always ensuring optimum clearance, which reduces wear on the cuttin~ edges 62 and 64.
Passage 164 provides venting for cylinder 144 when punch 66 is extencled to the position shown in Figure ~.
Upper forming die 170 is rigidly connecte~ to spindle 130 by retainin~ rod 172, which is threadedl~
secured at its lower end 174 to forming die 170, and is held against spindle 130 a~ its upper end by nut 176. Spindle 130 is connected to ~op plate 178 by screws 179, and plate 178 is connected to slide 24 by bolts 180 and nuts 182. Dowel 184 prevents rotation bet~een formin~ die 170 and spindle 130.
It will be noted that forming die 170 compri.ses an annular bead portion 186 around its periphery and an ~nnular groove 188 ad~acent bead 186.
With reference to Figure 5, the li~tout mechanis~
40 comprises a bracket 1~0 secured to the bed 14 of press 10 by bolts 192, which are received within sleeves 194 and held in place by nuts 196. Washers 197 and 198 are positioned between bolts 19~ and bed 14, and between nuts 196 and brac};et 190, xespectivel~.
aam sh~t ~0 i~ rotatably ~upportcd by hearing~
2~2 conn~ctecl to legr3 16 (Fi~ure 1), and te~mlnate~3 in ~3procket 4~, which is in enga~ement with chain ~2. Since chain ~2 i~ driven b~ ~prock~t 43, whlch i~ connected ko cr.mksha~t 1~, the rotation Oe cam : ~ ,' ' ,, :
-~ io ~ i sha~t 200 will be synchronized wi~h that o-E cranksha-Et 18 so that li.ftout occurs at the proper time in the press cycle. Cam 206 is connected to shaft 200 by an interference fit sleeve ~OA, which is scr~wed to cam 206. Sleeve 208 is connectecl to cam 206 by screws 210.
Cushion cylinder 212 is connected to the upper surace 213 of bracket 190 by screws 214, and includes a double ended cushion stem 216 connected to a piston ~not shown) within cylinder 212. Cylinder : 212, which is supplied with pressurized air from a suitable source of supply, exerts cons~ant downward pressure on stem 21fi. The lower end o~ stem 216 is threadedly secured tv follower yoke 218, and locked thereagainst by lock nut 220. Cam follower 222 is rotatably supported on shaft 224, the latter ~xtending through yoke 218 and secured thereto by nut 226.
As cam 206 is rotated, cam follower 222 will roll on its peripheral surface 228 and cause stem 216 to be lifted and lowered at the appropriate times in the press cycle.
The upper end oE stem 216 is connected to plat~
.24 by stem retainer 230, which is connected to plate 124 by screws 232. The lower end 234 o stem 92 i~ contacted by the upper sur~ace o~ plate 12~ when ~tem 216, yoke 21~ ancl followex 222 are pushed upwal.dly by cam 206.
With reference now to Ficlures ~, 3, 4 and 6, the operation o~ pr~ss 10 will be described. The steel or aluminum strip material 240 i~ advanced by ~eed meahani~m 36 ~o that an unblanked portion is po~i-tloned wi~hin ~he di~ ~et. r~eanwhlle, blankincJ
~lide ~1 and eormincJ ~ 24 ar~ movin~ downwa.rdly und~r tha aation o:~ cranksha~t 1~, wlkh blankinq ~l.id~ 21 leading eormincl ~lld~ 2~ sll~hkly a~ ~hown . . I
.
.5~3~4 in Figure 6. It will also he appreciated that the total travel of forming slide 24 is greater than the total travel oE blanking 51icle 21, a situakion which is necessitated hy the crreater travel requirea for the drawing operation.
As blan~in~ slide 21 moves downwardly, the lo~.~er edge of punch 66 will contact and re~t on the upper surface of strip material 240, hut no cu~ting of the strip material will occur at this time because blanking slides 21 and guide hushing 136 hava not yet caught up to punch 66. At a~proximately 140 of the pres~ c~cle, the ~urface 242 of quide bushing 132 will contact the upper surace of the piston portion 140 o~ punch 66 and drive cutting edge 64 1.5 downwardly past the cutting edge 62 of cutting die 58 so as to blank out a circular disk 84 rom the strip material 240. The press in thi~ position is illustrated in Figure 2 wherein the punch ~6 has just cut through the ~trip material 240.
Punch 66 continues to travel past cutting edge 62 by a slight amount to the bottom dead center posi tion illustrated in Figure ~. At the same time, forming slide 24 will cause the upper forming die 170 to pass by the lower edcre of punah 66 and draw the blank 84 to the shape illu~ratecl in Figure 3. In forminy this shape, beacl 186 pres~e~ liftout member 90 down-~ :
wardly against the action o~ liftou~ pins 112 and forms a bead 244 into the blank 84 a~ it passes into th~ annular ~pace b~tweon draw rin~ 54 and lower formin~ die 76. At the same time, groove 188 cooperate~
with bead 80 to form bead ~2.
Whil~ the draw.lncJ operation i-q ocaurrincr, blanklng ~llcle 21 h~gins to mov~ upwar~l~ a~ ~hown in Figux~, 6, but ~he aix pr~ure within c~llncler 144 hold~
the low~r ecl~Je o~ punch 66 acrain~t blank 8~ during at lo~t a portion o~ the drawin~ operatlon. Formin~
slide 24 then also be~ins to move upwardly at about the ~ame time that yuide bushing 136 begins to liEt punch 66, which is just a few degre~s past bottom dead center. Forming die 170 an~ punch 66 move upwardly together, and at the same time cam 206 begins to lii-t ~ollower 222, yoke 218, ~t(3m ~16, plate 124 and stem 92, which li~ts li~tout member ~6 and ~trips the part ~4 from lower die 76 to the position sho~7n in Fi~ure g. During strippin~ of part 84, both punGh 1~ 66 and upper forming die 170 ar~ maintained in close contact with part 84 so that maximum control is realized.
When part a4 has been lifted to the position shown in Fi~ure 4, it is eJected by a mechanical 15icker, or by a blast oE air, or by ~ravity, a~ in the case o~ an inclined press, or by a combination of any two or all three oE thas~ means.
As cam 206 continues to rotate, spring 94 will cause liftout member 86 to be re~racte~ below the tin line, and another segment of strip material 240 is fed into the die. The press then recycles to again perform the operations described above.
Although springs and pressuriz~d air have been used for various biasing functions i~ the press described above, in some cases thcy are interchangeable. For exrample, spring pre~sur~ could be utiliæed to bias punch 66 downwardlv rather than pres3urizecl air as in the preferred embodiment. The ball bearin~ as~embly 152 utili2ed to guide punch 66 can be any one o~
a variety oE commercially available bearings, such as those manuEaatured by Lempco Industrie~s Inc.
Althouc~h an open back inclinahl~, clouhl~ action pr~s 10 ha~ b~n d~scribed in connQctlorl with khe lnventlon, tha lnv~ntion i~ not c;o llmited to thi~
typ~ o~ pr~s~. E'urth~rmorc, th~ invantion could be utlllzecl ~or marlufacturincJ parts other than can .: ' ; , . .
S~3~1L4 ends, ancl the particular blanking and forming operations described a~ove are merely exemplar~ an~ are not intended to limit the invention in its ~roa~est orm.
Tlle invention also encompasses presses llaving a l~luralit~
of punches in the die set.
While this invention has been descxibed as having a preferred design, it will be understood that it is capa~le of further modification. This application is, therefore, intended to cover any variations, uses, or adaptations of the invention ~ollowin~ ~he ~eneral principles thereof and inc~udin~ such departures from the present disclosure as come ~it!~in ktlown or customar~ nractice in the art -to ~ ich this invention ~ertains and fall within the limits of the apnendecl claims.
. ."
18 to accomplish this rela~ive movement is within normal engineering expertise.
The shell ty~e bearincJ slaeves 30 are preerably pressure lubricated through pas~ages 32 connected s to a lubricant suppl~ (not shown).
Strip stock is fed into prPss 10 by fe2d 36, and the scrap is cut off by means o~ scrap cutter 38. A liftout mechanism 40 is clriven by means o chain, ~elt, or other power transmission 42, whicll is connected to sprocket 4 4 and to sprocket 43, the latter driv2n by cxanksha~t 18.
Re~erring now to Fi~ures 2, 3 and 4, ~he de~ails of the punch assembly will be described~ Bolst~r 46 is secured to bed 14 and lowex liftout pin retainer 1~ plate 48 is supported on the upper sllr~ace 4~ thereof.
Draw ring retainer 50 is supported on liftout pin retainer ~8, and serves to retain draw ring 52 in position. It will be noted that draw ring 52 includes an annular upstanding portion 54 around which cuttlng die retainer 56 is posi~ioned. Cutting die retainer 56 is secured to draw ring re~ainer 50, and includes an annular step 60 within which annular cutting die 58 is received. Cutting die 58 inclucles a cutting edge 62, which cooperates with ~he edga ~4 o~ ptmch 66 to stamp out a circular blank when p~nch 66 i~
driven downwardly past cutting edge 62, as wlll be described below. Filler plate 6n overlies and ls secur~d to die retainer plate 56, and the upper sur~ace 70 thereof supports the strip stock 240 as it is advanced through the press in a hoxizontal directionO
Cover plate 72 is rigidly sQcured in posltion/ and -~he lowe~ sur~ace 74 thereoe 1~ s~aced ro~ the upper ~r~ace 70 o~ r plate 68 ~o as to p~ovide a ,qubstantiall~ planar ~hannel ~hrou~h wlllch ~e ~toc]c material i~ ~d. The s~aae between ~ureac~ 70 and 74 generally de~ine~ what is known in the lnclu~try .
~L ~ o~314~
as the tin linel a hori~ontal o:r inclined plane -through which the strip stock is fed hy feed mechanism 36 (Fi~ure 1).
Lower forming die 76, the cross section of which S is circular in a plane parallel to th~ tin line, is connected to draw rinc3 52 by screws 78. Thus, draw ring retainer 50, clraw ring 52, lower formin~ :
die 76, pin retainer plate 48 and bolst~r 46 are rigidly connected to the press frame. ~ower forming dia 76 includes an annular bea~ portioll 80, which forms a corr~spondingly shaped bead 82 in the finished can end 84 illustrated in Figure 4~
Liftout element 86, which includes a generally circular base 88 and an upstanding annular rim portion 90, is sliclably received within draw ring 52 ~or reciprocating movement in the same direction as ~hs direction of movement of s1ides 21 and 24. Liftout member S8 is yieldably pulled downwardly by mean~
of liftout stem 92, which is threadedly secured to the base portion 88, and compression spring 94, which is disposed between the lower surfac2 96 of pin retainer plate 48 and a washer lQ0 held in place hy nut 102.
The holding force developeel by spring 94 can be adjusted by means of nut 102. ~i~tout member 86 slides around the lower portion 104 o~ lower forming die 76, and when retracted, its lower sur~ac~ 108 is in abutment with the upper surface l.L0 o~ draw rlng S2.
Li~tout member 36 is pushe~ to its lntermediate position by means o~ liEtout pins 112, which are .~0 slidably received in bushings 114 retained within pin retainer plate 4~ ietout pin~ :L12 are ~ressed upwardl!y h~ stems 116, which are ~onnected to piskolls (not shown~ wikhin pressur~ a~linders L18, the latter bf3~n~ khreadedly ~ecured to bolst~r 46 an~l seal~d 3S th~3rea(3a~llst b~ 0-~rin~s 120.A eluic1 passa(3e 1~2 ., ~ :
, . :
,- ~
:., .
.: . .
. . , :
is connected to a source of pressurized air to yieldably lift the blanked part against the actic)n of uppar die 170. It will be noted that the upper end of pin 112 engages the lower surface 10~ of liftout member 86 so as to raiYe liftout member 86 against the action of spring 94. Stem 92 is lifted by plate 124, which slides over screws 126 connected to bolster 46. Figure 3 illustrates plata 124 in its Eully retracted po~ition.
Turning now to the upper portion of the die set, a housing assembly 128 is slidably disposed with respect to spindle 130, and retains punch 66 fox slidable movement relative thereto. ~ou~ing a~sembly 12~ comprices a ~pindle alignment bearing 132 connected to slicle 21 by scraws 134, and a guide bushing 136 connected to spin~le alignment bearing by screws 138. The upper por-tion of punch 66 i~
for~ed as an annular piston 140 including seals 141 and 142, and reciprocat~s within an annular cylinder 144 defined by spindle alignment bearing 132 and an annular step in guide bushing 136. The intermediate portion 146 of punch 66 i~ annular and cylindrical in shape, and punch 66 includes a tapered transition portion 148 between intermediate portion 146 and the lower cutting portion 150 including cutting edge 64. Air pressure from passage 149 yiQldably and continuously urges punch 66 downwardly to the positlon o~ Figure 4.
Punch 66 i~ very accurately guided and aligned within guide bushing 136 by means of cylindrical ~all bearing as~embly 152, which comprise~ a cylindrical rat~iner h~ving a plurallty o~ ball b~aring~ 154 aaptu~cl therein. ~ portion of the hall bearings 1$4 ~x~ ln roll:lng enga~amant with the out~r cylindrical 3r~ ~ur~ace 156 o:E the in~ermediate p~r-tlon 146 o~ punch ' , ~ ;" ' ' ~''3~ 31~
66, and the remainder of the ball bearin~s 154 are in rolling engagement with the inner concave cylindrical sur~ace 153 of guide bushin~ 136. Bearing assembly 152 is held in place by bearing re~ainer 160, which 5 is secured to guide hushing 136 b~ screws 162. Bear-ing assembly 15~ is prPferably preloaded so that very precise tolerances can be maintained with respect to the position oE the punch 66 relative to cutting ; edge 62. As discussed above, this is important from the standpoint o~ always ensuring optimum clearance, which reduces wear on the cuttin~ edges 62 and 64.
Passage 164 provides venting for cylinder 144 when punch 66 is extencled to the position shown in Figure ~.
Upper forming die 170 is rigidly connecte~ to spindle 130 by retainin~ rod 172, which is threadedl~
secured at its lower end 174 to forming die 170, and is held against spindle 130 a~ its upper end by nut 176. Spindle 130 is connected to ~op plate 178 by screws 179, and plate 178 is connected to slide 24 by bolts 180 and nuts 182. Dowel 184 prevents rotation bet~een formin~ die 170 and spindle 130.
It will be noted that forming die 170 compri.ses an annular bead portion 186 around its periphery and an ~nnular groove 188 ad~acent bead 186.
With reference to Figure 5, the li~tout mechanis~
40 comprises a bracket 1~0 secured to the bed 14 of press 10 by bolts 192, which are received within sleeves 194 and held in place by nuts 196. Washers 197 and 198 are positioned between bolts 19~ and bed 14, and between nuts 196 and brac};et 190, xespectivel~.
aam sh~t ~0 i~ rotatably ~upportcd by hearing~
2~2 conn~ctecl to legr3 16 (Fi~ure 1), and te~mlnate~3 in ~3procket 4~, which is in enga~ement with chain ~2. Since chain ~2 i~ driven b~ ~prock~t 43, whlch i~ connected ko cr.mksha~t 1~, the rotation Oe cam : ~ ,' ' ,, :
-~ io ~ i sha~t 200 will be synchronized wi~h that o-E cranksha-Et 18 so that li.ftout occurs at the proper time in the press cycle. Cam 206 is connected to shaft 200 by an interference fit sleeve ~OA, which is scr~wed to cam 206. Sleeve 208 is connectecl to cam 206 by screws 210.
Cushion cylinder 212 is connected to the upper surace 213 of bracket 190 by screws 214, and includes a double ended cushion stem 216 connected to a piston ~not shown) within cylinder 212. Cylinder : 212, which is supplied with pressurized air from a suitable source of supply, exerts cons~ant downward pressure on stem 21fi. The lower end o~ stem 216 is threadedly secured tv follower yoke 218, and locked thereagainst by lock nut 220. Cam follower 222 is rotatably supported on shaft 224, the latter ~xtending through yoke 218 and secured thereto by nut 226.
As cam 206 is rotated, cam follower 222 will roll on its peripheral surface 228 and cause stem 216 to be lifted and lowered at the appropriate times in the press cycle.
The upper end oE stem 216 is connected to plat~
.24 by stem retainer 230, which is connected to plate 124 by screws 232. The lower end 234 o stem 92 i~ contacted by the upper sur~ace o~ plate 12~ when ~tem 216, yoke 21~ ancl followex 222 are pushed upwal.dly by cam 206.
With reference now to Ficlures ~, 3, 4 and 6, the operation o~ pr~ss 10 will be described. The steel or aluminum strip material 240 i~ advanced by ~eed meahani~m 36 ~o that an unblanked portion is po~i-tloned wi~hin ~he di~ ~et. r~eanwhlle, blankincJ
~lide ~1 and eormincJ ~ 24 ar~ movin~ downwa.rdly und~r tha aation o:~ cranksha~t 1~, wlkh blankinq ~l.id~ 21 leading eormincl ~lld~ 2~ sll~hkly a~ ~hown . . I
.
.5~3~4 in Figure 6. It will also he appreciated that the total travel of forming slide 24 is greater than the total travel oE blanking 51icle 21, a situakion which is necessitated hy the crreater travel requirea for the drawing operation.
As blan~in~ slide 21 moves downwardly, the lo~.~er edge of punch 66 will contact and re~t on the upper surface of strip material 240, hut no cu~ting of the strip material will occur at this time because blanking slides 21 and guide hushing 136 hava not yet caught up to punch 66. At a~proximately 140 of the pres~ c~cle, the ~urface 242 of quide bushing 132 will contact the upper surace of the piston portion 140 o~ punch 66 and drive cutting edge 64 1.5 downwardly past the cutting edge 62 of cutting die 58 so as to blank out a circular disk 84 rom the strip material 240. The press in thi~ position is illustrated in Figure 2 wherein the punch ~6 has just cut through the ~trip material 240.
Punch 66 continues to travel past cutting edge 62 by a slight amount to the bottom dead center posi tion illustrated in Figure ~. At the same time, forming slide 24 will cause the upper forming die 170 to pass by the lower edcre of punah 66 and draw the blank 84 to the shape illu~ratecl in Figure 3. In forminy this shape, beacl 186 pres~e~ liftout member 90 down-~ :
wardly against the action o~ liftou~ pins 112 and forms a bead 244 into the blank 84 a~ it passes into th~ annular ~pace b~tweon draw rin~ 54 and lower formin~ die 76. At the same time, groove 188 cooperate~
with bead 80 to form bead ~2.
Whil~ the draw.lncJ operation i-q ocaurrincr, blanklng ~llcle 21 h~gins to mov~ upwar~l~ a~ ~hown in Figux~, 6, but ~he aix pr~ure within c~llncler 144 hold~
the low~r ecl~Je o~ punch 66 acrain~t blank 8~ during at lo~t a portion o~ the drawin~ operatlon. Formin~
slide 24 then also be~ins to move upwardly at about the ~ame time that yuide bushing 136 begins to liEt punch 66, which is just a few degre~s past bottom dead center. Forming die 170 an~ punch 66 move upwardly together, and at the same time cam 206 begins to lii-t ~ollower 222, yoke 218, ~t(3m ~16, plate 124 and stem 92, which li~ts li~tout member ~6 and ~trips the part ~4 from lower die 76 to the position sho~7n in Fi~ure g. During strippin~ of part 84, both punGh 1~ 66 and upper forming die 170 ar~ maintained in close contact with part 84 so that maximum control is realized.
When part a4 has been lifted to the position shown in Fi~ure 4, it is eJected by a mechanical 15icker, or by a blast oE air, or by ~ravity, a~ in the case o~ an inclined press, or by a combination of any two or all three oE thas~ means.
As cam 206 continues to rotate, spring 94 will cause liftout member 86 to be re~racte~ below the tin line, and another segment of strip material 240 is fed into the die. The press then recycles to again perform the operations described above.
Although springs and pressuriz~d air have been used for various biasing functions i~ the press described above, in some cases thcy are interchangeable. For exrample, spring pre~sur~ could be utiliæed to bias punch 66 downwardlv rather than pres3urizecl air as in the preferred embodiment. The ball bearin~ as~embly 152 utili2ed to guide punch 66 can be any one o~
a variety oE commercially available bearings, such as those manuEaatured by Lempco Industrie~s Inc.
Althouc~h an open back inclinahl~, clouhl~ action pr~s 10 ha~ b~n d~scribed in connQctlorl with khe lnventlon, tha lnv~ntion i~ not c;o llmited to thi~
typ~ o~ pr~s~. E'urth~rmorc, th~ invantion could be utlllzecl ~or marlufacturincJ parts other than can .: ' ; , . .
S~3~1L4 ends, ancl the particular blanking and forming operations described a~ove are merely exemplar~ an~ are not intended to limit the invention in its ~roa~est orm.
Tlle invention also encompasses presses llaving a l~luralit~
of punches in the die set.
While this invention has been descxibed as having a preferred design, it will be understood that it is capa~le of further modification. This application is, therefore, intended to cover any variations, uses, or adaptations of the invention ~ollowin~ ~he ~eneral principles thereof and inc~udin~ such departures from the present disclosure as come ~it!~in ktlown or customar~ nractice in the art -to ~ ich this invention ~ertains and fall within the limits of the apnendecl claims.
. ."
Claims (13)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A double action press comprising:
a bed portion, a blanking slide, a forming slide, drive means connected to said slides for reciprocating said slides along respective rectilinear paths, said drive means comprising a crankshaft having at least two eccentrics thereon and at least two connecting rods connected to respective said slides and respective said eccentrics, said drive means causing said blanking slide to lead said forming slide, a forming die comprising a first forming tool element connected to said forming slide and a second forming tool element connected to the bed portion of the press, said tool elements adapted to coact with each other to form a part therebetween when brought together by said forming slide, a blanking die comprising a blanking punch connected to said blanking slide and a blanking tool element connected to the bed portion of the press, said punch and blanking tool element adapted to coact with each other to cut out a blank when brought together by said blanking slide at about the dead center position of the eccentric driving said blank-ing slide, said punch being reciprocally connected to said blanking slide for movement relative to said blanking slide in a direction parallel to the rectilinear movement of said blanking slide, said drive means causing said blanking slide to positively and non-yieldably engage said punch at about said dead center position of the eccentric driving said blanking slide to cut out a blank, and means for yieldably urging said punch in said rectilinear direction of said blanking slide away from said blankinq slide to extend relative to said blanking slide and exert a holding force on the blank as said blanking slide moves away.
a bed portion, a blanking slide, a forming slide, drive means connected to said slides for reciprocating said slides along respective rectilinear paths, said drive means comprising a crankshaft having at least two eccentrics thereon and at least two connecting rods connected to respective said slides and respective said eccentrics, said drive means causing said blanking slide to lead said forming slide, a forming die comprising a first forming tool element connected to said forming slide and a second forming tool element connected to the bed portion of the press, said tool elements adapted to coact with each other to form a part therebetween when brought together by said forming slide, a blanking die comprising a blanking punch connected to said blanking slide and a blanking tool element connected to the bed portion of the press, said punch and blanking tool element adapted to coact with each other to cut out a blank when brought together by said blanking slide at about the dead center position of the eccentric driving said blank-ing slide, said punch being reciprocally connected to said blanking slide for movement relative to said blanking slide in a direction parallel to the rectilinear movement of said blanking slide, said drive means causing said blanking slide to positively and non-yieldably engage said punch at about said dead center position of the eccentric driving said blanking slide to cut out a blank, and means for yieldably urging said punch in said rectilinear direction of said blanking slide away from said blankinq slide to extend relative to said blanking slide and exert a holding force on the blank as said blanking slide moves away.
2. The press of Claim 1 wherein the total rectilinear travel of said blanking slide is greater than the total rectilinear travel of said forming slide.
3. The press of Claim 2 wherein the press defines a generally planar feed path for strip stock between said first and second forming elements and between said punch and blanking tool element, and said first forming tool element travels through and past the plane of the feed path to a greater extent then does said punch.
4. The press of Claim 3 wherein the eccentric pertaining to said blanking slide is angularly offset relative to the eccentric pertaining to said forming slide to cause said blanking slide to lead said forming slide in both directions of the reciprocating movement thereof.
5. The press of Claim 1 wherein said blanking punch is slidable connected to said blanking slide, and said blanking tool element includes a cutting edge cooperating with the said punch to cut out a blank from stock fed into the press.
6, The press of Claim 5 wherein said cutting edge and punch encircle said forming die, and said drive means causes said punch and cutting edge to come together before said forming tool elements come together.
7. The press of Claim 6 wherein said means for yieldably urging causes said punch to exert a holding force on a blanked out part during at least a portion of the forming operation performed by said forming die.
8. The press of Claim 1 wherein said means for yieldably urging comprises a resilient medium inter-posed between said punch and blanking slide.
9. The press of Claim 8 wherein said means for yieldably urging comprises a piston and cylinder connected between said punch and blanking slide, and said resilient medium is a pressurized fluid in said cylinder.
10. The press of Claim 8 wherein a portion of said punch is formed as a piston which reciprocates within a cylinder in said blanking slide, and said medium is a pressurized fluid admitted into said cylinder.
11. The press of Claim 1 wherein said means for yieldably urging comprises a piston and cylinder connected between said punch and blanking slide, and means for admitting pressurized fluid into said cylinder.
12. The press of Claim 1 including a preloaded, antifriction bearing means interposed between said punch and said blanking slide for accurately guiding and aligning said punch relative to said blanking slide.
13. The press of Claim 1 wherein the total rectilinear travel of said punch is less than the total rectilinear travel of said blanking slide for each cycle of the press due to the reciprocal connection between said punch and blanking slide.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000432140A CA1178130A (en) | 1980-07-07 | 1983-07-08 | Double action press having floating punch |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US16596680A | 1980-07-07 | 1980-07-07 | |
| US165,966 | 1980-07-07 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000432140A Division CA1178130A (en) | 1980-07-07 | 1983-07-08 | Double action press having floating punch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1159314A true CA1159314A (en) | 1983-12-27 |
Family
ID=22601232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000376029A Expired CA1159314A (en) | 1980-07-07 | 1981-04-23 | Double action press having floating punch |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS5747599A (en) |
| CA (1) | CA1159314A (en) |
| DE (1) | DE3120887C2 (en) |
| FR (1) | FR2485988B1 (en) |
| GB (2) | GB2080173B (en) |
| IT (1) | IT1137278B (en) |
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|---|---|---|---|---|
| US4587826A (en) * | 1984-05-01 | 1986-05-13 | Redicon Corporation | Container end panel forming method and apparatus |
| US4903521A (en) * | 1988-09-02 | 1990-02-27 | Redicon Corporation | Method and apparatus for forming, reforming and curling shells in a single press |
| US5852970A (en) * | 1995-11-27 | 1998-12-29 | The Minster Machine Company | Underdrive opposing action press |
| CN104998946A (en) * | 2015-08-14 | 2015-10-28 | 南通茂溢机床有限公司 | Open type inclinable press |
| JP6626038B2 (en) * | 2017-06-07 | 2019-12-25 | アイダエンジニアリング株式会社 | Double blank detecting device for press machine and die protection device for press machine |
| CN108480446A (en) * | 2018-04-25 | 2018-09-04 | 苏州圣普亚精密机械有限公司 | Die mechanism |
| CN111570594A (en) * | 2020-05-22 | 2020-08-25 | 赖国梅 | Stamping device for automobile parts |
| DE102021126646A1 (en) * | 2021-10-14 | 2023-04-20 | MAIKO Engineering Gesellschaft mit beschränkter Haftung | Tool for forming coated sheet metal blanks |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA613455A (en) * | 1961-01-31 | O. Conner Guy | Anti-friction die set | |
| US1995357A (en) * | 1933-07-27 | 1935-03-26 | Western Electric Co | Apparatus for forming articles |
| US2411503A (en) * | 1941-01-03 | 1946-11-26 | Crown Cork & Seal Co | Cupping press |
| DE891684C (en) * | 1943-08-31 | 1953-10-01 | Hans Joachim Kuehne Dipl Ing D | Drawing press |
| CH534018A (en) * | 1970-04-08 | 1973-02-28 | Standun | Deep drawing press |
| FR2206166B1 (en) * | 1972-11-13 | 1976-01-30 | Solvay | |
| JPS529428B2 (en) * | 1973-02-06 | 1977-03-16 | ||
| US3902347A (en) * | 1973-10-23 | 1975-09-02 | Minster Machine Co | Mechanical press, especially a cupping press |
| DE2403532A1 (en) * | 1974-01-25 | 1975-08-07 | Schuler Gmbh L | DEVICE FOR LIMITING THE TRAVEL OF A PRESS SLOT |
| US3986382A (en) * | 1975-06-09 | 1976-10-19 | Gulf & Western Manufacturing Company (Hastings) | Horizontal can ironing press |
| US4020670A (en) * | 1976-03-19 | 1977-05-03 | Redicon Corporation | Triple action mechanism for producing high reduction cups in a double action press |
| IT1060911B (en) * | 1976-04-13 | 1982-09-30 | Sacmi | PRESS FOR SHEARING AND FORMING OF METAL BOWLS .... IN PARTICULAR OF PLUGS |
| US4080819A (en) * | 1976-11-26 | 1978-03-28 | Gulf & Western Manufacturing Company | Apparatus for making drawn articles |
| US4249410A (en) * | 1978-11-06 | 1981-02-10 | Standun, Inc. | Die press having selectively variable die access clearance |
-
1981
- 1981-04-23 CA CA000376029A patent/CA1159314A/en not_active Expired
- 1981-05-05 GB GB8113675A patent/GB2080173B/en not_active Expired
- 1981-05-26 DE DE3120887A patent/DE3120887C2/en not_active Expired
- 1981-07-06 JP JP56105429A patent/JPS5747599A/en active Granted
- 1981-07-07 IT IT22773/81A patent/IT1137278B/en active
- 1981-07-07 FR FR8113334A patent/FR2485988B1/en not_active Expired
-
1983
- 1983-07-28 GB GB08320378A patent/GB2122934B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| FR2485988A1 (en) | 1982-01-08 |
| DE3120887C2 (en) | 1986-09-04 |
| GB2080173B (en) | 1984-09-12 |
| GB2122934B (en) | 1984-10-24 |
| FR2485988B1 (en) | 1985-11-29 |
| JPS5747599A (en) | 1982-03-18 |
| JPS6315047B2 (en) | 1988-04-02 |
| IT8122773A0 (en) | 1981-07-07 |
| GB2080173A (en) | 1982-02-03 |
| DE3120887A1 (en) | 1982-03-18 |
| IT1137278B (en) | 1986-09-03 |
| GB2122934A (en) | 1984-01-25 |
| GB8320378D0 (en) | 1983-09-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |