US2644417A - High-speed double-action press - Google Patents

Description

July 7, 1.953 y v. GEQRGEFF 2,644,417`

HIGH-SPEED DOUBLE-ACTION PRESS Filed D60. A21, 1950 4 SheebS-Shet l I 6o l w /92 l 92 30 I f i l j. l '52 I A sa l 9o.

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HIGH-SPEED DOUBLE-'ACTION PRESS Filed Decv. 21,y 195o 4 sheets-sheet 4 o 4a 8o 12o 1 lo no 24o -280 32o aso INVENTOR.

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Patented July .7, 1953 UNIi-EvfisTATBS PATENT FICE.-

HIGH-SPEEDl lponeis-Ac'rioiv rfinisfsy Vasil George, La Grange Park, Ill., assignor to Danly Machine Specialties, Inc., Chicago, Ill.-,- a corporation oflilinois l Appiieation December 21, 195o, serii'No. 202,083

My invention action presses reduire comparatively large strokes.

ForA example, in a sixteen-inch ldraw a double action press of the prior art requires a stroke in the vicinity of thirty-seven inches for the The time required for moving the press parts through this long stroke circumscribes the number of operations which can be performed bythe press in a given Vperiod ottime. This is due to the fact that the .rate of draw is limited by the characteristicsv of thefmetal being drawn.l Every metal,as for example, steel, has a limit beyond which'itcannot be drawn cold. If it be attempted toA draw at a greater linear velocity than the critical velocity, the metal will tear. Accordingly,` greater output cannot be obtained by speeding the rotation of the press since this will result in the production of a linear drawing velocity beyond the critical velocity. It will be apparent, therefore, thatrin event it is desired to produce a large numberl of pieces within a given period of time, as is the case with presses forming part of a production line, it

becomes necessaryy to employV an increased number of presses. Double action presses vare large,

heavy and expensive pieces oi machinery and require not only'capital investment but factory space, as well'as maintenance expense in their upkeep.

I have been enabled to construct a double action press having a linkage'in which the press cycle is apportioned to'the'drawing operation'andwill consume a longer time than the return motion ci the innerl slide. A velocity o1" theinner slide :duringthe cyclej is greatly reduced. This enables meto speed up the press to a point within which the linear velocity of the draw is within the critical velocity and thus increase the output of the press. For example, my linkage is such that 225 ofthe 360 cycle is devoted to the downstroke while only 135 of rotation of the driving crank is devoted to the upstroke.v By thus lengthening the time of the idownstroke I havebeen enabledI to speend*adouble` In thisv manner" the linear i 2 Claims.v (Cl. 113-38)l action press capableV of seven strokes per minute to fourteen strokes per minute due to employing a construction having a slow drawing speed with respect to the returnspeed.vv f

'Some double action presses of "the vprior art employ two prime movers, one for the blank holder and one for the inner slide.A` Thisris due tothefact that the 'blank holder must dwell during the periodthe'inner slide does its Work. In my double action press a single prime mover is used to drive bothV the blank holder and the inner slide and a dwell is achieved by a linkage having small" amplitude of motion duringY the partof the cycle in which the'blank holder is to dwell, the blank holder and the inner slide beingv properly phased for the operation of thepress.

One object of my invention is to provide a double action-high speed press in which the number of strokes per unit of time performed by the press maybe increased without exceeding the rcritical maximum 'drawing velocity of the metal being worked uponbythe press. l

A further obJect of nay-invention isto provide a Vdouble action 'press which may be operated at a greatly increased speed in order to produce a greater rate ci work without exceeding the crtical linear velocity of draw of the metal being worked upon. .K Y. ,I

Another object of mylinvention is to provide a double action press employing a common prime mover for the blank holder andthe inner'slide.

Other and further obiects of my invention will appear from the following description.

In general, my invention contemplates -the provision of a press frame on which an inner slide and blank holder are mounted. A common prime mover Yand operating`V gearY train lare mounted adjacent the bottom of the press which may be installed in a pit, or the like. The prime mover drives a crank carrying a link. To the other end oiA the llink Ij pivot a high speed link, kone end of which is carriedby the frame. To the pin whichA is-driven by the crank link `and conned to ay predetermined locus by the high speed linkvI attach aconnecting rod :for driving the inner slide. The construction vis such. that the Y inner slide vwill move downwardlyl through 225 ciprocates a head which is linked to one of two yrockershaft,*armsin order Ato loscillate 'the rocker of the instant specification and which are to be read in conjunction therewith and'in which like reference numerals are used to indicate like parts in the various views:

Figure 1 is a sectional elevation showing a double action high speed press containing one embodiment of my invention. M' 7 Figure 2 is a sectional view taken along the line 2-2 of Figure 1. Figure 3 is a sectional plan View taken along Figure l is a motion diagram showing the moe tions of the inner slideY andthe blank Vholderv of aconventional doubleaction press.l

Figure 5 is a motion diagram similar to that shown in Figure 4, showing the motions vof the blank holder and the inner slidein apress according to the instant invention.'

More particularly,`vre ferr ing now to the drawings. my press comprises ya fr-ame'l ofany 'suitable .construction formedv fwelded steel plates hai/ins Straight sides. @1111.1 ellffd -1153i f dSL'Oi the like. Any suitable press frame 'may be'employed. As can be seen by reference to Figure .-j

2'. the frame is providedl .with Vfoo'tngs ladapted to support the press above a.n pitin which the driving train of the press is located. A 'prime mover, such as an electric rr'iotnlll, dri'v'ega flywheel I6 through Vf-belts I8. is adapted to be clutched to a shaft" 2'0 which carries a pinion 22 for rotation therewith. The vpinion drives a gear 24 carried ybyand secured to a shaft 26. Secured lto the shaft Zlfforrota- .tion -therewithfare a pair" of pinions 28" which mesh with a .pair of .gears @TAS/5.1111109 Seen .bY reference to Figure 1 there are'map'air of gears 30, one disposed on each side 'of the center line of the press. For purposes ofl convenience, the drives will -be described with respect to one side only'f since the construction is` symmetrical and in all .respects thesame on both sides ofthe press and like reference numerals wiilbe used for the corresponding parte .O11 OPPOSte' sides Gf. the press. The gear `3 0 is secured to a shaft 32Y which is formed Ywith a pair rof bearing disks'34 mounted in suitable bearings in the press'fraine. The center of the bearing disk 34 is coaxialV with the .center line of the 'shaft 32. Extending between the bearing disksyeccentric of their axes of rotation I provide a crankpin 36 around 'which is positioned one end of a link 33. The other .end of link 38 carries apli/ot pin 4 8 Yaround which .I pivot ,one end Of .the high `speed link V42, vthe otherend of which is pivotally positioned to the frame by means of pin 44 carried by the frame. Around the pin is also positioned the lower end of a ,connecting rod 4.6, the other end of ,which `is connected to Va reciprocating head .by ,means of p in 58. A plurality of rods 52 secure the inner slide l54 to the reciprocating head`48 for movement therewith. The upper 4ends of .rods 52 are provided with threads 56 vadapted to engage Athe nuts positioned within housings .60. VThe arrangement is such .thatlthe vposition of the slide 54 can be adjusted withespect vto The flywheel the frame by the rotation of the nuts coacting with the threaded portions 56 of the rods 52.

The outboard disk 34 is formed with a crankpin 62 carrying the lower end of a connecting rod 64. The upper end of the connecting rod 64 is connected to a pin 66 carried by a reciprocating head 68. A pair of rocker shafts 'l0 are carried'by the frame. Secured to each rocker shaft for rotation therewith I vprovide'a rocker crank V'li and a rocker arm 14. Each rocker crank 'l2 is connected to the reciprocating head 68 by a link 16 which extends between a pin 18 carried by the head 68 and a pin 80 carriedat the end of recker crank 12. `As the reciprocating head reciproeates .the rocker shaft 'l0 will rock, moving the ends of rocker cranks 12 downwardly. As the head 68 continues to move downwardly the link 'I6 will be substantially horizontal and the rocker crank 'l2 will be substantially vertical. In .this position movement of the head 68 will produce vnegligible oscillation of the rocker shaft due to the fact .that in the vicinity of 'zero degrees a vaiat'ionof the angle willv 'produce 'substanltially no ch-angein the`length of the cosine. The rotation of the rocker crank 1 2 will produce a corresponding rotation of the rocker arm '14. Theend of the rocker arrnl'd carries a pin 8 2 aroundwhich the lower endof connecting link 84 is pivoted. Thefother end 'of c onnecting link 84 is secured by pivot Din 8 6 to a reciprocating head 88I 'Rods 98 secure the head 88 vtothe blank holder 92 by means of adiustableeonnectionsV 94. As the ends of rocker varms"'l4 move'downwardly the blank'hlder Vwill move downwardly. When the arm 1 4extendssubstantially vertically'the links 84 will likewise 'behsiibstantially vertical, making an angle'of 3.60. withthe rocker arms 14'. In this position rotation yofthe rocker arm will produce substantially'no movement of the blank holder. The phasing pf 'the'parts' is such that when the crankp'in 62 reaches'V bottom dead centerpall of the parts will bein the'vicinity of their Smau ampiitdde of motiopositions vse that .the blank holder will dwell.V Actually A'the' Vblank holder will oscillate .very slightly .through an'arnpiitude of approximately 10.03v inch' a umbefof v1 ',irnes as each of thelirkagespasses and V'repa'ssje's its .dead .center .13.0511111211 *The 'amplitude 0f 11161- .tion is well within .the elongationof the metal vof the linkages so that the blank holderwill rest 1.111111011211013' while the 1.1.1116? .Slide @des its Work Referring now .to Figure 2, itwill'be seenthat the .cran-knip 3 6 is approaching the top of'its stroke, .the direction of rotation beine ifi a lOkwise direction as .viewed in this figure. During 225 rotation from the tondead Center .the 11.111?" slide will move ,downward-.1y at .a comparatively slow speed. The ,curve ,of .motion @an be 56.61.1105 reference to Figure 5. Bottom dead center 'is reached ,at .approximately 225 of the press cycle. Duringr the remainder .of 1,35?, of the press cycle. .the inner slide will move Aunllhl-rdly starting slowly and .then moving extremely rapidly 4Vto top dead center. The. phasing of .the high speed link 42 and the connecting link 3.8 is such that lthis result is accomplished. The time gained in the rapid return v'of the inner slide is used to reduce the velocity of the inner slide during its downstroke. VIn this manner I am enabled to increase the speed of rotation of the press without exceeding the criticaldrawing speed. The results of mydnvention can -b'es't be seen by comparing the Vinner slide curve shown in 'Figure 4 of the conventional press which moves l'with simple harmonic motion with the curve of motion of my press shown in Figure 5.

The blank holder moves rapidly downwardly until the linkages approach their small amplitude of motion positions and then dwells during the period in which the inner slide does its work. After bottom dead center is reached both the blank holder and the inner slide move upwardly rapidly.

It will be seen, further, that I use advantageously a common prime mover and phase the motion of parts so that they are always correct for the operation of the press. A conventional double action press having an inner slide capacity of 700 tons, a blank holder capacity of 500 tons, an inner slide stroke of 28 inches and a blank holder stroke of approximately 18 inches was designed to run at seven strokesv per minute to draw a particular metal. A high speed double action press of my design having precisely the same capacity was able to run at fourteen strokes per minute, doubling the output of the press without exceeding the critical drawing velocity for the particular metal.

It will be seen that I have accomplished the a pair of crank arms carried by the rocker shaft for rotation therewith, a link extending between the reciprocating head and one of the crank arms and forming a first toggle linkage therewith, means carried by the blank holder for movement therewith and a connecting link extending between said last named means and the other of the crank arms forming a second toggle linkage therewith', said toggle linkages being constructed and arranged to arrive at their small amplitude of motion positions at substantially ther same time as said second crankpin approaches its bottom dead center whereby to cause the blank holder to dwell while the slide is performing its work.

2. A high speed Adouble action power press including in combination a frame, a slide mounted on the frame for reciprocation with respect thereto, a blank holder mounted on the frame for reciprocation with respect thereto, a crankshaft formed with a pair of cranks, means for rotating objects of my invention. I have provided a double action high speed press in which the number of strokes per unit of time performed by the press maybe substantially doubled without exceedingthe maximum drawing velocity of the metal being worked upon by the press. I have provided a double action press invvhich the draw starts comparatively slowly, thus minimizing the tendency of the metal to tear. I have provided a double action press capable of increased output employing a common prime mover for the blank holder and the inner slide.

It willV be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of my claims. It is further obvious that various changes may be made in details within the scope of my claims without departing from the spirit of my invention.- It is therefore to be understood that my invention is not to be limited to the specific details shown and described.

Having thus described my invention, what I claim is:

1. A high speed double action power press including in combination a frame, a slide mounted for reciprocation on the frame, a blank holder mounted for reciprocation on the frame, a primer mover, a, crankshaft formed with a pair of crankpins, means for driving the crankshaft from the prime mover, a link havingone end thereof pivotally carried by one of the crankpins, a second link having one end thereof pivotally secured to the press frame, a pin pivotally interconnecting the other ends of the rst and second links, a connecting rod extending between the last named pin and the slide, a reciprocating head, a connecting rod extending between the second crankpin andthe reciprocating head, a rocker shaft,

the crankshaft, a pair of links and a connecting rod having one of respective ends pivotally connected at a common center, means for pivotally connecting the other end of one of the links to the press frame, means for connecting the other end of the other of the links to the rst of said cranks, means for connecting the other end of the connecting rod to the press slide, a reciprocating head, a connecting rod between the other of said cranks and the head, a rocker shaft carried by the frame formed with a pair of crank arms, a link connecting the reciprocating head I with one of the crank arms, means carried by the blank holder for movement therewith, and a link connecting said last named means with the other of the crank arms,the first of said last namedA links and the rst of the said crank arms forming a toggle linkage, the second of said last named links and the second of the crank arms forming References Cited inthe le of this patent UNITED STATES PATENTS Number Name Date 1,025,154 Orton May '7, 1912 1,423,617 Klocke July 25, 1922 1,871,088 Seidel et al. Allg. 9, 1932 1,888,450 Byerlein Nov. 22, 1932 2,364,661 Rode et al. Dec. 12, 1944 2,522,746 Byerlein Sept. 19, 1950 2,550,061 Glasner Apr. 24, 1951 2,550,063 Johansen Apr. 24, 1951 2,550,064 Ward Apr. 24, 1951

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