US3147695A

US3147695A - Adjustable stroke mechanism

Info

Publication number: US3147695A
Application number: US213694A
Authority: US
Inventors: Jules K Hyman
Original assignee: Individual
Current assignee: Individual
Priority date: 1962-07-31
Filing date: 1962-07-31
Publication date: 1964-09-08
Anticipated expiration: 1981-09-08

Description

SPt 8 1964 .1. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM Filed July 3l, 1962 11 Sheets-Sheet l 35 Z5 f I I .4A L6 L7 Jams K.// /MAN ATTORNEYS.

Sept. 8, 1964 J. K. HYMAN ADJUSTABLE STROKE MECHANISM 1l Sheets-Sheet 2 Filed July 51, 1962 INVENTOR- Jw f5 K. /Y/W/W ATTORNEYS.

sept. s, 1964 Filed July 3l, 1962 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM 11 Sheets-Sheet 3 INVENTOR.

ATTGRNEYS.

Sept 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM Filed July 31, 1962 11 Sheets-sheet 5 44 o 47 o 44 42 4.2 4l. 315 4/34 as [5l sa' "e "J4 'Z5 gg if jJ/'La p4 92 F70. 6 auf; /yMA/v BW ATTORNEYS.

Sept. 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHAN ISM Filed July 51, 1962 1l Sheets-Sheet 6 HG. 7 /1/f5 /CHYMA/v www ATTORNEYS.

Sept. 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STRKE MECHANISM INVENTOR.

f/z/Es KHYMAN EXW M ATTORNEYS.

Sept. 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM mvENToR.

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Sept. 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM Filed July 31, 1962 11 sheets-sheet 9 I NVENTOR Lzum K. /YMA/v -G-y/ WMM ATTORNEYS.

Sept 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM Filed July 31, 1962 11 Sheets-Sheet l0 INVENTOR Y/m f5 K /1 YAM/V Sept. 8, 1964 J. K. HYMAN 3,147,695

ADJUSTABLE STROKE MECHANISM l Q5, l

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INVENTOR. /0f5/(.HYMAA/ United States Patent O 3,147,695 ADSUSTAELE STRKE MECHANISM Jules K. Hyman, 625 Burnham Road, Philadelphia, Pa. Filed .liuly 31, 1962, Ser. No. 213,694 Claims. (Cl. 10U-257) This invention relates to an adjustable stroke mechanism and although hereinafter described and shown in conjunction with a metal stamping press, has broad applicability to any mechanism wherein a variation in the stroke of a reciprocating member is desirable, as for example, all types of reciprocable presses, punches, stamping machines, pumps, piston driven engines, as well as other piston actuated types of mechanism and the like.

A primary object of this invention is the provision of a stroke adjusting mechanism for a reciprocating member whereby the length of the stroke may be varied from zero or any other minimum length through an unlimited or infinite number of lengths of strokes to the maximum capacity of the particular installation wherein the device is employed.

A further object of this invention is the provision of a mechanism of this character which requires only rotational relative movement between cylindrically shaped parts which exert pressure on each other through appropriately shaped bearings when the machine which has the adjustable stroke mechanism incorporated therein is required to exert a pressure or other force, thus obviating any linear sliding relative movement between stressed parts.

An additional object of the invention is the provision of such a mechanism wherein the mid stroke position or either stroke end position of the driven parts may be precisely duplicated with any stroke as adjusted, for an unlimited number of strokes, since the adjustable portion of the mechanism remains stationary relative to whichever position has been selected to be duplicated during the actual adjustment of the stroke.

A further object of the invention is the provision of a mechanism of this character wherein the maximum force transmitted by the driving mechanism is always transmitted through the stroke adjusting mechanism in a direction approximating almost exactly the required guided direction of travel of the driven parts.

A still further object of the invention is the provision of a mechanism of this character which is so designed that the locking of the adjustable parts in position through positive locking means is not mandatory since the force vectors of the stresses in the apparatus constructed in accordance with the instant invention are calculated in directions such that none tend to exert force on the mechanism in a direction tending to change the setting.

A still further object of the invention is the provision of a mechanism of this character so arranged that in all positions of adjustment the power output of the apparatus with which the mechanism is associated is characterized by a mechanical multiplication rather than a diminution of the initial power input, since the diminution of the stroke by the mechanism of the instant invention tends to increase the power capacity of the apparatus with which it is associated.

A more specific object of the invention is the provision of a device of this character having particular utility in conjunction with a cam or eccentric driven reciprocatory member wherein the stroke adjustment is eifectuated by varying the location of the fulcrum of a driving lever to lengthen or shorten the stroke and decrease or increase, by mechanical multiplication the input force exerted by the driving mechanism for the cam without the necessity of altering or changing the length of the crankshaft or the lever by which the stroke is performed.

"ice

Still another speciiic object of the invention is the provision of an adjusting mechanism of this character which may be employed in conjunction with presses, stamping machines, or similar apparatus which will vary the capacity of the machine in tons of pressure by such minute alteration of the length of the power stroke as to render the range of the machine within the limits of its capacity variable substantially to an infinite degree thus permitting the use of a wide variety of dies, stamps, punches, and the like, for operation upon an unlimited variety of materials offering a wide range of resistance without altering either the crankshaft or the driving lever.

A further and more speciiic object of the invention is the provision of a mechanism of this character which has particular applicability to metal stamping presses operable at a wide range of speeds from extremely slow to extremely fast incorporating a stationary bed or platen and a parallel reciprocating ram or piston which will press, squeeze, push, pull, impart a blow or exert any other reciprocably applied force for the purpose of forming, shaping, compressing, stretching, expanding, contracting, shearing, severing or otherwise similarly treating any desired article of any shape, size, or material susceptible to such treatment within the capacity of the machine, by appropriate variation of the stroke length, and the consequent force exerted thereby through a virtually infinite range.

A further important object of the invention is the provision of a mechanism in association with such a press wherein the reciprocable element may be adjusted so that the reciprocating member is always in identical position at the bottom of its stroke regardless of the variation in the length or the stroke, or, alternatively, in precisely the same location at the top of its stroke regardless of the adjustment and the consequent force exerted by change in the length of the stroke, thus rendering the apparatus of the instant invention readily applicable to mechanism wherein the reciprocating member is either above or below the adjusting mechanism.

A still further object of the invention is the provision of a mechanism of this character which can vary the length of the stroke of a reciprocating member of a machine while the machine is operating and the member is in motion, because the adjusting controls for the mechanism are not fastened directly to any parts of the mechanism which are moved by any movable parts of the machine, because the adjusting controls can be located on the exterior of the machine and because the adjusting controls do not need to be locked in position through positive locking means since the force vectors of the stresses in the mechanism constructed in accordance with the instant invention are calculated in directions such that none tend to exert force on the controls in a direction tending to change the setting.

A further speciiic object of the invention is the provision, in association with a metal stamping press of the character hereinafter described embodying the stroke adjusting mechanism of the instant invention, of a pneumatic counterbalance incorporated directly into the press and comprised of basic parts of the press modified so that, in effect the normal operating mechanism forms its own counterbalance.

Still other objects of the invention reside in the cornbinations of elements, arrangements of parts, and features of construction.

Other objects will in part be obvious and in part be pointed out hereinafter and shown in the accompanying drawings wherein there is illustrated one embodiment of the instant inventive concept.

In the drawings:

FIGURE 1 is a front elevational View of one form of a metal stamping press embodying a stroke adjusting mechanism illustrative of the principles of the instant inventive concept, and including a self-contained counterbalance feature, certain concealed parts .thereof being indicated in dotted lines..

FIGURE 2 is a side elevational view of the structure of FIG. 1, as viewed from the left, certain concealed parts also being indicated in dotted lines.

FIGURE 3 is a rear elevational view, portions of the mechanism being broken away for the sake of clarity of illustration, and certain concealed parts being shown in dotted lines.

FIGURE 4 is a sectional view taken substantially along the line 4 4 of FIGURE l as viewed in the direction indicated by the arrows.

FIGURE 5 is a top plan view taken substantially along the line 5 5 of FIGURE 4, showing certain constructional details, and omitting parts o-f the mechanism.

FIGURE 6 is a sectional view taken substantially along the line 6 6 of FIGURE 1 as viewed in the direction indicated by the arrows.

FIGURE 7 is a sectional view taken substantially along the line 7 7 of FIGURE 1 as viewed in the direction indicated by the arrows.

FIGURE 8 is a sectional view taken substantially along the line 8 8 of FIGURE 2 as viewed in the direction indicated by the arrows.

FIGURE 9 isa sectional view taken substantially along the line 9 9 of FIGURE 1 as viewed in the direction indicated by the arrows.

FIGURE 10 is a sectional view taken substantially along the line lil-lll of FIGURE 1 as viewed in the direction indicated by the arrows.

FIGURE 11 is an enlarged fragmentary sectional view taken substantially along the line 11 11 of FIGURE 8 as viewed in the direction indicated by the arrows.

FIGURE 12 is an enlarged detailed sectional view taken substantially along the line 12-12 of FIGURE 8 as viewed in the direction indicated by the arrows.

FIGURE 13 is an enlarged detailed sectional view taken substantially along .the line 13 13` of FIGURE 8 as viewed in the direction indicated by the arrows.

FIGURE 14 is a detailed sectional View taken substantially along the line 14-14 of FIGURE 11 as viewed in the direction indicated by the arrows.

FIGURE 15 is a side elevational view partly in section showing a modified form of crank arm construction.

FIGURE 16 is a front view of the crank arm of FIG- URE 15.

FIGURE 17 is a sectional view taken substantially along the line 17 17 of FIGURE 15 :as viewed in the direction of the arrows.

FIGURE 18 is a bottom plan view of the crank arm of FIGURE 15.

FIGURE 19 is a sectional view taken substantially along the line 19 19 of FIGURE 15 as Viewed in the direction indicated by the arrows.

FIGURES 20, 21, and 22 are diagrammatic views illustrative of certain stroke lengths obtainable by the apparatus illustrating the principle of operation thereof; and

FIGURES 23, 24 and 25 are diagrammatic views simirlar to FIGURES 20, 2l, and 22 disclosing certain other operative positions of the adjusting mechanism which may be obtained by changing the effective length of the crank arm.

Similar reference characters refer to similar parts throughout the several views of the drawings.

Having reference now to the drawings in detail, there is generally indicated at 25 a metal stamping press constructed in accordance with the instant invention. Press 25 comprises a base plate 26 upon which is mounted a frame, generally indicated at 27, and to be more fully described hereinafter. Plate 26 is supported by leveling screws 28, one of which is positioned at each corner thereof, the leveling screws extending through the plate, and being held in proper adjusted relation by means of upper and lower adjusting nuts 29 and 3), respectively. Leveling screws 28 have enlarged lower extremities 31 which have secured thereto pads 32 of suitable vibration absorbing material. Leveling screws 28 permit the machine to be mounted in such manner that bed plate 34 can ybe made level even though a supporting floor F might not be level.

The top 33 of frame 27 has fixedly secured thereto a bed plate 34, which in turn supports a bolster 35. Top 33 and bed plate 34 are provided with aligned

openings

36 and 37, respectively, adjacent each corner thereof, each pair of aligned openings containing a guide bushing 38. Each guide bushing 38 has a top llange 39 which rests on the top of bed plate 34, and upon which rests a rod dus-t seal 4t), secured in position by a rod guide retainer 41, all as best shown in FIGURE 4.

Pull rods 42 extend through each guide bushing, and are reciprocable therein in a manner to be more fully described hereinafter.

Each pull rod 42 is provided adjacent its top with a threaded portion 43 upon which is mounted a ram leveling nut 44. A slightly reduced smooth portion 45 of each rod 42 extends through a tightly fitted opening 46 in each corner of a ram 47. Additionally, reduced threaded portions 48 of rods 42 extend above the openings 46 with ram level lock nuts 49 tightly securing the parts in related assembly. Each rarn level nut 44 may be individually adjusted to level ram 47 in absolute parallelism with bolster 35. Ram 47 may be of any desired conventional .conguration but in the illustrative embodiment of the instant invention shown, includes longitudinally extending reinforcing ribs 5t) on its upper surface as well as transverse strengthening and reinforcing ribs 51, as best shown in FIGURES 4 and 5. Raised annuli 52 may surround each opening 46 to ensure firm and level engagement of lock nuts 49. A die of positive design is normally fastened to the underside of the press ram and a `die of negative design is normally fastened to the top side of the bolster plate, both dies aligned with one another and fastened by means of clamps or screws in holes tapped into the ram and bolster especially for that purpose. Such holes are not shown in the drawings because they are usually located to suit the set of dies. Material to be shaped is then placed upon or passed between the dies which are forced to open and close alternately and thus to cut or otherwise change the shape of the material.

The lower ends of rods 42, which extend substantially to the bottom of frame 2'7 are reduced as indicated at 53, and force fitted through openings 54 in a plate 55, the latter serving as a portion of the connection between the pull rods and the driving mechanism in a manner to be more fully described hereinafter.

Reduced ends 53 below plate 55 are surrounded by piston members 56, which are reciprocable in lower guide bushings 57 which are inserted in openings 58 in base plate 26. The lower portions of bushings 57 are flanged as at 59 and secured to the underside of base plate 26 by means of screws 60;

Each piston member 56 is provided at its lower end with a recess 61 for the reception of a fastening nut 62 mounted on the threaded extremity 63 of each reduced portion 53, and lbeneath each fastening nut is positioned a locking nut 64 similarly threaded. Appropriate bushing seals 68, piston seals 65, and rod seals 66 are provided, and a suitable rod washer 67 seats in the base of each recess 61.

Counterbalancing of the mechanism associated with the rods 42 is effected by compressed air in counterbalance tanks 7?, the tanks being provided with flanges 71 which are secured by means of screws or bolts 72 to ribs 73 depending from the underside of base plate 26. Compressed air is supplied to tanks 78 through inlets 74 which extend to a suitable air compressor (not shown) or other suitable source of compressed air. The size of tanks '70, and the pressure of the compressed air contained therein may vary as conditions warrant. In the apparatus herein shown and described, and based on the assumption that each piston assembly is five inches in diameter giving a total piston area of approximately 78 square inches, it has been found that air pressure of approximately 100 pounds per square inch will support or counterbalance approximately 7,800 pound of mechanism. The pressure may obviously be varied in accordance with the weight of the assembly which it is required to counterbalance.

4 Plate 55 carries on its upper surface a pair of aligned oppositely disposed lugs 75, which are secured thereto as by means of bolts '76 or the like. Each lug 75 is apertured as at 77 for the reception of a pivot pin 78 which also extends through aligned apertures in depending lugs 79 which in turn depend from ram height adjusting boxes 8?. Ram height adjusting boxes 80 serve pivotally to connect through wrist pins 78, plate 55, and hence pull rods 42 and ram 47 with a pair of aligned ram height adjusting links 81. The function and operation of ram height adjusting boxes 80 will be more fully described hereinafter.

At their upper ends each adjusting link 81 extends between a pair of yoke arms 82 and is pivotally connected therebtween by means of a yoke connection pin 83 mounted in a suitable bearing or bushing 84. Each pair of yoke arms S2 extend from the ends of a yoke block 85, the central portion of which is provided with a pair of spaced openings for the reception of heavy guide rods 36. j Guide rods or bars 86 are secured to yoke block 85 by means of nuts 87. At their opposite ends rods 86 extend through aligned openings in a lower hinge leaf 90A, beyond which is positioned a yoke screw stabilizer plate 88, having openings therein through which rods 86 extend, the assembly being firmly secured by stabilizer lock nuts 39. Lower hinge leaf 90A is secured through a hinge pin 90 to an upper hinge leaf 911B, through suitable openings in which extend a pair of spaced upper guide bars 91. Upper guide bars 91 also extend through openings in the upper portion of frame 27 and are secured in position by upper guide rod or bar retainers 92 which are secured in turn by screws 93 to the exterior of the face of the frame.

Yoke block 85 also has a lug or arm 94 projecting at an angle opposite to the yoke arms 82, to the opposite sides of which are secured a pair of second links 95 by means of yoke pins or pivots 96 mounted in bushings 97.

The opposite ends of second links 95 are connected by pins 9S movable in bushings 99 to one end of a lever 10i), it being understood that such levers 1011 and their associated components are provided in duplicate on opposite sides of the assembly.

Each lover 1011 is pivotally mounted on `a pivot pin or fulcrum 101 mounted in bearings or bushings 102 which extend between spaced supporting lugs 103 carried by the underside of top 33 of frame 27. The opposite end of each lever 1110 is pivotally connected as by a pivot pin 104 mounted in bushings or bearings 105 between the bifurcated ends 106 of crankshaft arms 107.

It should here be pointed out that pins 98, 101, and 104 are all in aligned relation as are

pins

83, 96, and hinge pin 90. It will also be seen that crankshaft arm 107 reciprocates, the reciprocation being effected in a manner to be more fully described hereinafter in a vertical direction to oscillate levers 1110 about their fulcrurn pins 101. Due to the constant lengths of second links 95, pin 96 and pin 83 are similarly moved, in conjunction with yoke block S5 about hinge pin 91B as a fulcrum Thus, variation of the distance between hinge pin 90 and pin 83 will vary the distance of movement of pin 83, and consequently link 81, plate 55, pull rods 42 and ultimately ram 4'7. The structure for varying the distance between hinge pin and pin 83, and hence the effective stroke of ram 47, will be more fully described hereinafter.

The two crankshaft arms 197 are simultaneously moved by means of a crankshaft 10S which extends transversely across the base of the frame and is mounted in bushings or bearings 1tl9 carried by bearing blocks 116 which are carried by the end walls 112 of frame 27 and intermediate partitions 113, the arrangement being such that there is a bearing block on each side of each crankshaft arm. Bearing blocks are provided with bearing caps 114 secured to the bearing blocks by means of screws 115, the caps being on the outer side of the frame to facilitate the removal or interchange of crankshaft 1198 when necessary or desirable. Crankshaft arms 107 are provided at their lower ends with connecting bushings 116 which surround eccentrics 117 on shaft 10S. Connection caps 118 are provided for crankshaft arms 107, and held in'position by screws 119, so that the crankshaft arms may also be readily removed from the apparatus if desired.

A motor bracket 120 supports an electric motor 121, which through a suitable pulley 122 and drive belts 123, drives a fly wheel 124 which in turn through a conventional clutch 125 and brake 126, drives crankshaft 108.

Referring back now to the ram height adjustment housings 80 and having particular reference to FIGURES l1 to 14, inclusive, and more particularly to FIGURE 13, it will be seen that each housing contains a worm nut which is rotatable by worm 131 mounted on a worm shaft 132 which is rotatably mounted in

bushings

133 and 134. One end of shaft 132 is squared at 135 and extends through the face 136 of the adjacent bushing 134. Screws 137 serve to hold the outer bushing in position around the shaft. Thrust bearings 138 are positioned at opposite ends of the worm, to minimize friction between the ends of the worms'and bearings.

The lower portion of worm nut 136 is provided with teeth 139 engageable by the worm 131 while the upper portion thereof is provided with vertical slots 140. The interior of nut 131) is threaded and engages the lower threaded end 141 of links S1 (see FlG. 6). When locking means, to be more fully described hereinafter, compressing the nut 130 by means of its slots'about threaded portion 141, are not operative, it will be seen that rotation of shaft 132 by means of a suitable crank or the like will, through worm 131 and worm gear teeth 139, rotate nut 130 to move housing 80 vertically with respect to the threaded end 141 of link 31. Such vertical movement will in turn move plate 55 and pull rods 42 vertically to adjust the position of ram 47 relative to the bolster- 35. After such adjustment has been achieved, however, it is necessary to lock the nut 130 against inadvertent or accidental turning, it being noted that such turning can be effected only through worm 131. The locking means take the form, as best shown in FIGURE 11, of locking splits or slots 142 in a locking block 143 secured to the cover 144 of housing 80. Cover 144 is secured in position by means of screws 145.

Transversely extending bolts 146 extend through aligned bores in the opposite split portions of member 143, so that when screws 146 are tightened, the slots 142 close effectively to close the slots 14) and clamp the nut 130 about threaded end 141 in such manner that rotation thereof either by means of a crank applied to squared end 135, the shaft 132, or any other means, is positively precluded. A pin 146a extends through locking block 143 and cover 144 being press tted into suitable aligned openings to prevent turning of block 143 when bolts 146 are loosened.

Loosening of bolts 146, however, releases the pressure locking nut 130 to reduce threaded portion 141, and permits linear adjustment of the parts in the manner previously described, thus serving to adjust the position of ram 47.

The two housings 80 and their associated links 81 are connected by means of a coupling shaft 147 which is connected to the opposite worm shafts 132 by means of interlocking coupling sleeve 148 having oppositely positioned fingers 149 thereon, and keyed as by means of keys 148e to the adjacent ends of the worm shafts 132 and coupling shaft 147. It is to be .noted that only one of the housings 80 is provided with a squared end of the shaft, this being the one most accessible to the operator for use.

Referring back now to the means for varying the relative distance between hinge pin 90 and wrist pin 83, in order to vary the effective stroke of rarn 47, it will be seen that upper guide rods 91 extend through openings in depending

portions

150 and 151 of frame 27 which are carried by top wall 33. Rods 91 are retained in fixed position at one end by the previously mentioned guide bar or rod retainers 92 and at their other ends, after passing through a partition 152 apertured to receive their ends, abut against the inner wall 153 of a generally channel-shaped stroke adjustment gear train bracket, generally indicated at 154, and having side wall portions 155. An upper adjusting screw 160 having a smooth portion 161 engages in a threaded bore 162 in upper hinge leaf 90b, the smooth portion 161 extending through an upper screw guide 162a in partition or depending lug member 150. A bearing 163 extends through an opening in end wall 152, as well as inner bracket wall 153 and is provided with a thrust bearing 164 and a lock nut 165. The smooth portion 161 reduced as at 166 extends through a bearing or bushing 167 in a vertical partition 168 comprising a part of bracket 154. A thrust bearing 169 and a lock nut 170 hold portion 166 in position. The outer end of reduced portion 166 carries a worm gear 171. It will thus be seen that rotation of worm gear 171, in a manner to be fully described hereinafter, serves to move upper hinge leaf 90b between

partitions

150 and 151.

A second screw 172 engages in a threaded bore 173 in lower hinge leaf 90a. Screw 172 has a smooth portion 174 which extends through a suitable opening in stabilizer 8S and is provided with a thrust bearing 175 and a lock nut 176.

During an adjustment of the stroke, lower hinge leaf 90a and upper hinge leaf 90b move simultaneously because of their connection through hinge pin 90. While at the point of the stroke which is to be duplicated (in this illustrative embodiment of the invention, the bottom) yoke block 85, and more specifically, pin 96 must always remain in the same position relative to the vertical center line of frame 27 as viewed in side elevation. Screw 172, being restricted from longitudinal movement in yoke block 85 serves to accomplish this because its thread has the same pitch and lead as screw 160.

When screws 160 and 172 are rotated at the same rate of speed, in a manner to be more fully described hereinafter, screw 172 travels through lower hinge leaf 90a with the same speed at which upper hinge leaf 90b, hinge pin 90 and lower hinge leaf 90a are traveling, but in the opposite direction. This serves to eliminate, by counter effect, any longitudinal dislocation of screw 172 or any parts attached thereto, especially yoke block S5. In other Words, even though hinge leaf 90b may carry hinge leaf 90a forward or backward, neither screw 172 nor yoke block 85 will be dislocated in either direction. Screw 172, therefore, has as its primary function the maintaining of the position of yoke block 85 and pin 96 at al1 times.

The travel of lower hinge leaf 90a is limited at one end by a stabilizer S8 and at its other end by yoke block 85, the arrangement being such that lower hinge plate 90a may travel between the opposite pairs of yoke arms 82 to a position wherein pin 90 is in alignment with pin 83, at which point the stroke of ram 47 will be zero, as will be more fully explained hereinafter.

The opposite end of screw 172 is smooth as indicated at 177 and extends through a yoke screw bushing 178 in a suitable central bore in yoke block 85. A yoke thrust bearing 179 engages in an enlarged portion 180 of the bore, and is held by a flange 181 on the end of smooth portion 177. A universal joint assembly 182 is secured to the head or flange 181, and extends into a telescopic sleeve 183 to which it is also secured. A telescopic shaft 134 is linearly movable within sleeve 183 and is in turn connected to a second universal assembly 185, which is provided with a shaft 186 which extends through a suitable bushing 137 in partition 168. A second worm gear 188 is provided on the extremity of shaft 186.

It will now be seen that when identical worm gears 171 and 138 are rotated simultaneously, the hinge assembly comprised of hinges a and 90b and hinge pin 90 will move as a unit along the threaded length of screws and 172. As hinge pin 90 approaches pin S3, the stroke of ram 47 will be reduced, and as pin 90 is moved away from pin 83, the stroke of ram 47 will be increased, as will be pointed out hereinafter.

Means are provided for simultaneous rotation of worm gears 171 and 188, and take the form of identical upper and

lower worms

190 and 191, respectively.

Worms

190 and 191 are mounted on

shafts

192 and 193 which extend through suitable openings in

horizontal partitions

194 and 195, respectively, suitable conventional thrust bearings and bushings being provided for the support of the shafts.

Shafts

192 and 193 are connected by and keyed to a coupling 196, the shaft 193 carrying a miter gear 197. Miter gear 197 is enmeshed with a second miter gear 198, the hub of which extends through a face plate 200 and carries exteriorly thereof a gear 201 which has a square central opening 202 therein. The square hole 202 is adapted for the reception of the squared end 203 of a crank handle 204. Rotation of crank handle 204 will thus obviously rotate the

screws

160 and 172 to move upper and

lower hinge plates

90b and 90a transversely of the apparatus.

A locking pinion 205 may, if desired, be provided on plate 200 enmeshed with gear 201 and provided with a socket head screw 206. When screw 206 is tightened, pinion 205 will be precluded from rotation, and consequently gear 201 cannot be turned. When the screw 206 is loosened, however, gear 201 is free to rotate and through the mechanism previously described, to rotate the

screws

160 and 172. Such a locking pinion is, however, optional since the nature of the mechanism renders locking unnecessary and, if desired, a plain disc may be substituted for gear 201 and pinion 205 omitted entirely.

FIGURES 20, 21, and 22 illustrate schematically the operation of the device. In FIGURE 20 the parts are shown at substantially maximum position, in accordance with the disclosure of the apparatus in the previously described form thereof. As here shown, hinge pin 90 is closely adjacent stabilizer 88, and is linked by the yoke assembly 85 and guide bars 86 with pin S3. The distance between

83 and 96 is fixed by the yoke assembly while links 95 retain the position of

pins

96 and 98 in constant relation. Fulcrum pin 101 is also fixed, as is the distance between pin 101 and wrist pin 104, which is connected to crank arm 107 which is in turn connected to eccentric member 117. The pivotal mounting of link 81 at 83 and its secondary pivotal mounting at 78 permit reciprocal movement of plate 55 and hence pull rods 42 through the distance indicated by dotted lines in the operation of the apparatus, so that a substantially maximum length of stroke of ram 47 is permitted. In FIGURE 21 hinge pin 90 has been moved, by the previously described rotation of

screws

172 and 160, t0 any one of an infinite number of intermediate positions, and the stroke has been reduced. FIGURE 22 shows a position of hinge pin 90 closely adjacent its limit of travel which is defined by the position of the edge of yoke block 85, the corresponding travel on screw 160 being limited by the face of lug 150, which, when the parts are in horizontal relation as shown, are in alignment. The positions of FIGURES 2l and 22 are illustrative of the multiplicity of stroke adjustments which may be accomplished by the mechanism hereinbefore described, it being readily apparent that when the hinge pin 90 is in aligned relation between the pins 83, the eifective stroke of plate 55, and hence ram 47, will be zero. It is to be noted that with this arrangement pin 83 and hence plate 55 and consequently ram 47 are always in precisely the same location at the bottom of the stroke despite the distance of hinge pin 90 from pin 83. It is to be noted that crankshaft 108 should be located so that eccentric 117 assumes its top position when lever 100 is substantially perpendicular to the center line of crank arm 107 in order to produce a resultant force which is substantially perpendicular to lever 100 at pin 96.

However, by changing the length of the crank arm, in a manner to be more fully described hereinafter, a different type of stroke may be achieved as shown in FIG-

URES

23, 24, and 25. ln this arrangement hinge pin 90, when extended to substantially its maximum position adjacent stabilizer or stop 88, serves as a fulcrum for a downward movement of

pins

83 and 96 and hence link 81 and its associated plate 55. With the parts so arranged, the ram may be made to duplicate its position at the top of a substantially infinite number of diiferent strokes. It may here be pointed out that in the position to be duplicated the line between

points

96, 83, and 90 must be parallel to the screw 160. It is to be noted that by changing the length of crank arm which can be made adjustable either the top, bottom, or midstroke position of the ram may be duplicated.

FIGURES l5 to 19, inclusive, disclose a modied form of crank arm generally indicated at 10741, which is adjustable and which may be substituted for the crank arms 107 in order to effectuate the abovementioned top, bottom, or midstroke position duplication. Crank arm 107a is comprised of an upper section 207, the top of which is bifurcated as at 208, to provide upstanding portions 209 having apertures 210 in aligned relation therein. The portions 209 extend upwardly on opposite sides of levers 100 and are secured thereto by means of pins 104 as in the case of the previously described crank arrn 107. A threaded bore 211 in the bottom of upper section 207 is threaded with a left hand thread to accommodate a corresponding left-hand thread 212 on an adjusting screw generally indicated at 213. The central portion of adjusting screw 213 is enlarged as at 214, to form a ilange having openings 215 therein which may be engaged by a tool for turning the screw. The opposite end of the screw is right-hand threaded as is the bore 217 in the top 218 of a lower section 219. The bottom of lower section 219 is apertured as at 220, the aperture containing a connection bushing 221 which also fits within a corresponding semi-circular aperture in a connection cap 222 which is secured as by means of screws 223 to the lower end of lower section 219. Bushing 221, connection caps 222, and screws 223 are substantially identical to the previously described bushings 116, connection caps 118, and screws 119 and serve to secure the crank arm 107:1 to the crank shaft 108 in a manner identical to that previously described.

The left-hand threaded portion 212 of adjusting screw 213 is provided with a left-hand threaded lock nut 224 provided with openings 225 for the reception of a tool for turning the same, while the lower or right-hand threaded portion 216 of adjusting screw 213 is provided with a right-handed hand threaded lock nut 226 provided with turning openings 227. The arrangement is thus such that by release of the

lock nuts

224 and 226 and turning of screw 213 by means of enlarged portion or flange 214, the effective length of the composite crank arm 107a comprised of upper and lower sections 207 10 and 219, may be suitably adjusted to vary the effective length of the crank arm, and hence eifect the desired duplication of the top, bottom, or midstroke position of the ram.

Adjustment of a stroke by means of this mechanism can be made while the mechanism is in any position. However, in order to calculate the correct length of crank arm 107 or to adjust crank arm 107a to the correct center distance between pin 104 and eccentric 117, then the center line of pin 96, pin 83, and hinge pin should be moved to a position parallel to screw 160, and the crank shaft rotated until the center of the eccentric 117 falls on a center line common to pin 104 and shaft 108. When using a driving mechanism such as the one herein illustrated, if eccentric 117 is placed above shaft 108 for the aforementioned calculations, then the position of the ram at the bottom of the stroke will be duplicated precisely. If eccentric 117 is placed on the extended center line below shaft 108, then the top of the stroke position will be precisely duplicated. If crank arm 107 is made, or crank arm 107a is adjusted so that the center distance between pin 104 and eccentric 117 duplicates the center distance between pin 104 and shaft 108, then the mid stroke position of the ram will be duplicated exactly.

An object of this invention has been described as the provision of a mechanism of this character which is so designed that the locking of the adjustable parts in position through positive locking means is not mandatory. The self-locking means for moving the fulcrum 90 consist of the

Worms

190 and 191 and the mating worm gears 171 and 188. They are self-locking, especially if the worms are of the common single-threaded type and have a small lead, because while the worms are able to rotate the worm gears in order to accomplish the adjustment, the worm gears are not able to rotate the worms in order to disturb the adjusted setting. Also, rotating the screw will move the fulcrum 90, but no conceivable movement of 90 could rotate 160.

The lever assembly referred to in the claims is the group of parts numbered 82 through 94, 96, 97 and 172 through 181. These parts, as assembled, form an adjustable lever, the basic elements of which are the yoke pins 96, the yoke connecting pins 83, and the hinge pins 90. This lever assembly is shown in FIGURES 20 through 25 simply as the

lever

96, 83, 90.

In the claims, the means which pivotally connect one end 96, of the lever assembly to the other end 104, of the crank arm, consists of the second links 95, pins 98, and the levers 100. The pivots are the connecting pins 83, which are at an intermediate point on the lever assembly, and the movable fulcrum is the hinge pin 90, which is adjustably positioned between pivots 83 and the other end 88, of the lever assembly. The links are the adjustable links 81, and the reciprocating member is the plate 55.

The stroke of the reciprocating member is the distance between the two extreme positions assumed by that member when it is forced to travel from one position to the other by a cycling of the driving mechanism. Such a cycle in the machine illustrated herewith would be embraced by a 360 rotation of the crankshaft. The distance between the two extreme positions, assumed by the reciprocating member, can be adjusted, i.e., shortened or lengthened, by means of the stroke adjusting mechanism presented herewith.

The adjustment of the length of the stroke should not be confused with the positioning of the reciprocating member and, consequently, the ram. The positioning adjustment in the subject machine is presented as the ram height adjusting mechanism, which allows the correct spacing between the ram and the bolster plate. In effect, the ram height adjustment permits the movable upper die to be located a-t the correct distance from the stationary lower die, and the stroke adjustment permits the movable die to travel various prescribed distances toward and away from the stationary die.

Prom the foregoing it will now be seen that there is herein provided an improved adjustable stroke mechanism which may be advantageously employed with a wide variety of apparatus, and which through herein shown in conjunction with a particular type of press, is adaptable to many other similar applications, which accomplishes all the objects of this invention, and others, including many advantages of great practical utility and commercial importance.

As many embodiments may be made of this inventive concept, and as many modifications may be made in the embodiment hereinbefore shown and described, it is to be understood that all matter herein is to be interpreted merely as illustrative, and not in a limiting sense.

I claim:

1. Mechanism for varying the length of the stroke ot a reciprocating member driven by a rotary eccentric from zero through an infinite number of different stroke lengths to a predetermined maximum length, comprising an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, and means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from Zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly.

2. Mechanism for varying the length of the stroke of a reciprocating member driven by a rotary eccentric from `zero through an infinite number of dierent stroke lengths to a predetermined maximum length, comprising an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, said means connecting said one end of said lever assembly to said other end of said crank arm Comprising a second link pivoted at one end to said one end of said lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever xed on said lever at a dsitance from the center of said pivotal connection at said one end of said lever which is equal Ato half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection at said other end of said lever.

3. Mechanism for varying the length of the stroke of a reciprocating member driven by a rotary eccentric from zero through an infinite number of different stroke lengths to a predetermined maximum length, comprising an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally :connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected :at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an innite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, Said means connecting said one end of said lever assembly to said other end of said crank arm comprising a second link pivoted at one end to said one end of said firstmentioned lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever iixed on said lever at a distance from the center of said pivotal connection at said one end of said lever which is equal to half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection at said other end of said lever, and means for varying effective length of said rst-mentioned link to vary the terminal position of said reciprocating member.

4. Mechanism for varying the length of the stroke of a reciprocating member driven by a rotary eccentric from zero through an infinite number of different stroke lengths to a predetermined maximum length, comprising an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end 4of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, said means connecting said one end of said lever assembly to said other end of said crank arm comprising a second link pivoted at one end to said one end of said lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever fixed on said lever at a distance from the center of said pivotal connection at said one end of said lever which is equal to half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection at `said other end of said lever, and means whereby the position of said reciprocating member can be precisely duplicated at either top, bottom or mid-point of said stroke, upon repetition of said stroke, regardless of adjusted variations of said stroke.

5. In a press, the combination of a frame, a xed platen having openings therethrough carried by the top of said frame, a reciprocating ram positioned above said platen, pull rods extending through said openings and connected at one of their ends to said ram land linearly movable in said frame, a plate connected to the other ends of said pull rods, means for reciprocating said plate, and means for varying the length of the reciprocating stroke of said plate from zero through an inlinite number of stroke lengths to a predetermined maximum stroke length, whereby the position of said plate can be precisely duplicated at either the top, bottom or midpoint of said stroke, upon repetition of said stroke, regardless of adjusted variations of said stroke, said last mentioned means including an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned be-tween said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, said reciprocating member fastened to said plate for reciprocation thereof, and means for moving said fulcrurn from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from Zero when said fulcrum 4is concentric with said pivot through an ininite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly.

6. In a press, the combination of a frame, a xed platen having openings, therethrough carried by the top of said frame, a reciprocating ram positioned above said platen, pull rods extending through -said openings and connected at one of their ends to said ram and linearly movable in said frame, a plate connected to the other ends of said pull rods, means for reciprocating said plate, means for varying the length of the reciprocating stroke of said plate from zero through an infinite number of stroke lengths to a predetermined maximum stroke length, whereby the position of said plate can be precisely duplicated at either the top, bottom or midpoint of said stroke, upon repetition of said stroke, regardless of adjusted variations of said stroke, said last mentioned means including an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, -a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, said reciprocating member fastened to said plate for reciprocation thereof, and means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, said means connecting -said one end of said lever assembly to said other end of said crank arm comprising a second link pivoted at one end to said one end of said lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever iixed on said lever at a distance from the center of said pivotal connection at said one end of said lever which is equal to half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection at said other end of said lever.

7. In a press, the combination of a frame, a lixed platen carried having openings therethrough by the top of said frame, a reciprocating ram positioned above said platen, pull rods extending through said openings and connected at one of their ends to said ram and linearly movable in said frame, a plate connected to the other ends of said pull rods, means for reciprocating said plate, means for varying the length of reciprocating stroke of said plate from zero through an infinite number of stroke lengths to a predetermined maximum stroke length, whereby the position of said plate can be precisely duplicated at either the top, bottom or midpoint of said stroke, upon repetition of said stroke, regardless of adjusted variations of said s-troke, said last-mentioned means including an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, .a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, said reciprocating member fastened to said plate for reciprocation thereof, and means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, said means connecting said one of said lever assembly to said other end of said crank arm comprising a second link pivoted at one end to said one end of said lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever fixed on said lever at a distance from the center of said pivotal connection at said one end of said lever which is equal to half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection .at said other end of said lever, and means whereby the position of said reciprocating member can be precisely duplicated at either top, bottom or mid-point of said stroke, upon repetition of said stroke, regardless of adjusted variations of said stroke.

8. In a press, the combination of a frame, a iixed platen having openings therethrough carried by the top of said frame, a reciprocating ram positioned above said platen, pull' rods extending through said openings and connected at one of their ends to said ram and linearly movable in said frame, a plate connected tothe other ends of said pull rods, means for reciprocating said plate, means for varying the length of the reciprocating stroke of said plate from zero through an innite number of stroke lengths to a predetermined maximum stroke length, whereby the position of said plate can be precise-V ly duplicated at either the top, bottom or midpoint of said stroke, upon repetition of said stroke, regardless of adjusted variations of said stroke, said last-mentioned means including an eccentric, means for rotating said eccentric, a crank arm, means connecting one end of said crank arm to said eccentric for reciprocation thereby, a lever assembly, means pivotally connecting one end of said lever assembly to the other end of said crank arm, a pivot at an intermediate point on said lever assembly, a movable fulcrum for said lever assembly normally positioned between said pivot and the other end of said lever assembly, a link connected at one end to said pivot, a reciprocating member pivotally connected to the other end of said link, said reciprocating member fastened to said plate for reciprocation thereof, means for moving said fulcrum from said other end of said lever assembly towards and away from said pivot to vary the stroke of said reciprocating member from zero when said fulcrum is concentric with said pivot through an infinite number of stroke lengths to maximum length when said fulcrum is adjacent said other end of said lever assembly, said means connecting said one end of said lever assembly to said other end of said crank arm comprising a second link pivoted at one end to said one end of said lever assembly, a lever, means pivotally connecting the other end of said second link to one end of said lever, a pivotal connection between the other end of said lever and said other end of said crank arm, and a fulcrum for said lever iixed on said lever at a distance from the center of said pivotal connection at said one end of said lever which is equal to half of or less than half of the total distance between said center of said pivotal connection at said one end of said lever and said pivotal connection at said other end of said lever, means for varying the effective length of said first-mentioned link to vary the terminal position of said reciprocating member, and means for varying the effective length of said crank arm whereby said terminal position may be either at the top, bottom, or mid-point of the said stroke.

9. In a press, the combination of a frame, a fixed platen having openings therethrough carried by the top of said frame, a reciprocating ram positioned above said platen, pull rods extending through said openings and connected at one of their ends to said ram and linearly movable in said frame, a plate connected to the other ends of said pull rods, a ram height adjusting box pivotally secured to saidY plate, a driving link having one end adjustably mounted in said box, a yoke block, yoke arms extending from said block, a pivotal connection between said yoke arms and the other end of said driving link, a hinge assembly comprising a hinge pin and upper and lower hinge leaves, a stabilizer plate, lower guide rods fixed in said yoke block and said stabilizer plate, said lower hinge leaf having apertures therein slidably mounting said lower hinge leaf on said lower guide bars, upper guide bars fixed to the underside of the top of said frame, said upper hinge leaf having apertures therein slidably mounting said upper hinge leaf on said upper guide bars, an additional arm carried by said yoke block extending in a direction angularly disposed relative to said yoke arms, a connecting link pivotally connected at one end to said additional arm, a lever pivotally connected at one end to the other end of said link, a fulcrum for said lever secured to the underside of the top of said frame, a crank arm, a pivotal connection between the other end of said lever and said crank arm, a crankshaft mounted in said frame for reciprocating said crank arm to oscillate said lever and swing said lower hinge leaf about said hinge pin to Areciprocate said ram through said pull rods, means for driving said crankshaft, and means for moving said hinge pin and said upper and lower hinge leaves linearly along their respective guide rods to vary the position of said hinge pin relative to said pivotal connection between said yoke arms and said other end of said driving link to vary the distance of reciprocating movement of said plate and hence the stroke length of said ram.

10. The invention as set forth in claim 9 wherein said last-mentioned means comprises a pair of threaded members, one extending through a threaded opening provided in said upper hinge leaf, and the other extending through a threaded opening in said lower hinge, and means for simultaneously rotating both of said threaded members.

11. The invention as set forth in claim 10 wherein said other threaded member includes a pair of telescoping sleeves and a universal joint on each side of said sleeves to accommodate the oscillatory movement of said lower hingle leaf when said crank arm is operated.

12. The invention as set forth in claim 10 wherein said means for simultaneously rotating said threaded members comprise a worm gear on the end of each threaded member, a worm engaging each worm gear, a single shaft carrying both of said worms, a miter gear carried by said shaft, a second miter gear engaging said rstmentioned miter gear, and a removable crank for manually rotating said second miter gear.

13. The invention as set forth in claim 12 wherein lock means are provided for said second miter gear.

14. The invention as set forth in claim 13 wherein said lock means include a at gear concentric with and secured to said second miter gear, a locking pinion gear in mesh with said ilat gear, and means clamping said pinion gear against rotation.

15. The invention as set forth in claim 9 wherein said ram height adjusting box includes upper and lower openings through which said one end of said driving link extends, said one end being reduced and threaded, a split clamping nut in said box engaging said reduced threaded end of said driving link, worm gear teeth cut peripherally on said clamping nut, a worm in said box engaging said worm gear teeth, external removable crank means for rotating said worm, and means for locking said clamping nut against rotation.

16. The invention as set forth in claim 15 wherein said last-mentioned means include slots in said box, said box being comprised of two separable pieces with said slots therebetween, and bolts engaging threaded bores in one of said separable pieces and extending through aligned bores in the other of said separable pieces for compressing said slots to compress said split clamping nut to preclude rotation thereof on said threaded end of said driving link.

17. In a press, the combination of a frame, a xed platen having openings therethrough carried by the top of said frame, a reciprocating ram positioned above said platen, pull rods extending through said openings and connected at one of their ends to said ram and linearly movable in said frame, a plate connected to the other ends of said pull rods, a ram height adjusting box pivotally secured to said plate, a driving link having one end adjustably mounted in said box, a yoke block, yoke arms extending from said block, a pivotal connection between said yoke arms and the other end of said driving link, a hinge assembly comprising a hinge pin and upper and lower hinge leaves, a stabilizer plate, lower guide rods fixed in said yoke block and said stabilizer plate, said lower hinge leaf having apertures therein slidably mounting said lower hinge leaf on said lower guide bars, upper guide bars iixed to the underside of the top of said frame, said upper hinge leaf having apertures therein slidably mounting said upper hinge leaf on said upper guide bars, an additional arm carried by said yoke block extending in a direction angularly disposed relative to said yoke arms, a connecting'link pivotally connected at one end to said additional arm, a lever pivotally connected at one end to the other end of said link, a fulcrum for said lever secured to the underside of the top of said frame, a crank arm, a pivotal connection between the other end of said lever and said crank arm, a crankshaft mounted in said frame for reciprocating said crank arm to oscillate said lever and swing said lower hinge leaf about said hinge pin to reciprocate said ram through said pull rods, means for driving said crankshaft, means for moving said hinge pin and said upper and lower hinge leaves linearly along their respective guide rods to vary the position of said hinge pin relative to said pivotal connection between said yoke arms and said other end of said driving link to vary the distance of reciprocating movement of said plate and hence the stroke length of said ram, said last-mentioned means comprising a pair of threaded members, one extending through a threaded opening provided in said upper hinge leaf, and the other extending through a threaded opening in said lower hinge leaf, means for simultaneously rotating both of said threaded members, said other threaded member including a pair of telescoping sleeves and a universal joint on each side of said sleeves to accommodate the oscillatory movement of said lower hinge leaf when said crank arm is operated, said means for simultaneously rotating said threaded members comprising a worm gear on the end of each threaded member,

a worm engaging each worm gear, a single shaft carrying both of said worms, a miter gear carried by said shaft, a second miter gear engaging said rst-mentioned miter gear, and a removable crank for manually rotating said second miter gear, lock means for said second mter gear, said lock means including a flat gear concentric with and secured to said second miter gear, a locking pinion gear in mesh with said flat gear, means clamping said pinion gear against rotation, said ram height adjusting box including upper and lower openings through which said end of said driving link extends, said one end being reduced and threaded, a split clamping nut in said box engaging said reduced threaded end of said driving link, worm gear teeth cut peripherally on said clamping nut, a worm in said box engaging said worm gear teeth, external removable crank means for rotating said worm, means for locking said clamping nut against rotation, said last-mentioned means including slots in said box, said box being comprised of two separable pieces with said slots therebetween, and bolts engaging threaded bores in one of said separable pieces and extending through aligned bores in the other of said separable pieces for compressing said slots to compress said split clamping nut to preclude rotation thereof in said threaded end of said driving link.

18. The invention as set forth in claim 17 wherein a piston is provided on the lower end of each pull rod, said frame having bored apertures through which said pistons extend, compressed air counterbalance tanks beneath said base, and means for supplying compressed air to said tanks to counterbalance said pull rods, said ram and said means for varying said length of said reciprocating stroke of said plate and said ram.

19. The structure of claim 1 wherein said mechanism is provided with a stationary frame, and wherein the means for moving said fulcrum are supported by said frame independently of the operative parts of said mechanism, whereby said fulcrum may be adjusted during the operation of the mechanism.

20. The structure of claim 19 wherein said means for moving said fulcrum include self-locking means whereby the necessity for positive locking of said means for moving said fulcrum is eliminated, the force vectors of the operating components of said mechanism being exerted in directions such that none tend to exert force on said means for moving said fulcrum in a direction tending to change the setting of said self-locking means.

References Cited in the file of this patent UNITED STATES PATENTS 617,147 Dewes et al. Jan. 3, 1899 1,009,528 Cruse Nov. 14, 1911 1,749,398 Strout Mar. 4, 1930 2,310,890 Brandes Feb. 9, 1943 2,378,062 Byerlein June 12, 1945 2,475,693 Borzym July 12, 1949 2,841,991 Saalfrank July 8, 1958 2,984,175 Wahl May 16, 1961 3,051,078 Webster Aug. 28, 1962 FOREIGN PATENTS 479,526 Great Britain Feb. 7, 1938 577,247 Germany May 29, 1933 1,050,812 Germany Sept. 9, 1953 242,666 Switzerland May 31, 1946

Claims

1. MECHANISM FOR VARYING THE LENGTH OF THE STROKE OF A RECIPROCATING MEMBER DRIVEN BY A ROTARY ECENTRIC FROM ZERO THROUGH AN INFINITE NUMBER OF DIFFERENT STROKE LENGTHS TO A PREDETERMINED MAXIMUM LENGTH, COMPRISING AN ECCENTRIC MEANS FOR ROTATING SAID ECENTRIC, A CRANK ARM, MEANS CONNECTING ONE END OF SAID CRANK ARM TO SAID ECCENTRIC FOR RECIPROCATION THEREBY, A LEVER ASSEMBLY MEANS PIVOTALLY CONNECTING ONE END OF SAID LEVER ASSEMBLY TO THE OTHER END OF SAID CRANK ARM, A PIVOT AT AN INTERMEDIATE POINT ON SAID LEVER ASSEMBLY, A MOVABLE FULCRUM FOR SAID LEVER ASSEMBLY NORMALLY POSITIONED BETWEEN SAID PIVOT AND THE OTHER END OF SAID LEVER ASSEMBLY, A LINK CONNECTED AT ONE END OF SAID PIVOT, A RECIPROCATING MEMBER PIVOTALLY CONNECTED TO THE OTHER END OF THE SAID LINK, AND MEANS FOR MOVING SAID FULCRUM FROM SAID OTHER END OF SAID LEVER ASSEMBLY TOWARDS AND AWAY FROM SAID PIVOT TO VARY THE STROKE OF SAID RECIPROCATING MEMBER FROM ZERO WHEN SAID FULCRUM IS CONCENTRIC WITH SAID PIVOT THROUGH AN INFINITE NUMBER OF STROKE LENGTHS TO MAXIMUM LENGTH WHEN SAID FULCRUM IS ADJACENT SAID OTHER END OF SAID LEVER ASSEMBLY.