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Publication numberUS3371513 A
Publication typeGrant
Publication dateMar 5, 1968
Filing dateDec 9, 1965
Priority dateDec 9, 1965
Also published asDE1552017A1, DE1552017B2, DE1552017C3
Publication numberUS 3371513 A, US 3371513A, US-A-3371513, US3371513 A, US3371513A
InventorsAchler Howard S, Harold Kaufmann
Original AssigneeKaufmann Tool & Engineering Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Open end rolling machine
US 3371513 A
Abstract  available in
Images(3)
Previous page
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Claims  available in
Description  (OCR text may contain errors)

March 5, 1968 H. S. ACHLER ET AL OPEN END ROLLING MACHINE Filed Dec. 9, i965 FIGI 5 Sheets-Sheet l NVENTORS HOWARD S. ACHLER 'y HAROLD KAUFMANN BY @wf/ :fl

55M ATTORNEYS March 5, 1968 A H. s. ACHLER ET AL 3,371,513

OPEN END ROLLING MAQVJ'IINIS! INVENTORS HOWARD S. ACHLER HAROLD KAUFMANN BY 972%4 y '/WMTTORNEYS March 5, 1968 H. s. AcHLl-:R ET Al. 3,371,513

' O-PEN END ROLLING MACHINE Filed Dec. 9, 1965 5 Sheets-Sheet 5 YIO A DMn-|006 lood IOOd` |oob ' |42 52 22) BY 9b |60 TToRNEYs United States Patent tice 3,371,5l3 Patented Mar. 5, 1968 3,371,513 GEEN END ROLLING MACHINE Howard S. Achler and Harold Kaufmann, Chicago, Ill.,

assignors to Kaufmann Tool & Engineering Corp., Chicago, Ill., a-corporation of Iliinois Continuation-impart of application Ser. No. 357,413,

Apr. 6, 1964. This application Dec. 9, 1965, Ser.

ABSTRACT F 'fl-lia` DESCLSURE An elongated roller having anti-deflection character so as to a'void Ibowing when uniformly loaded is provided -at relatively low cost by locating the support bearings, for a sleeve dening the pressure-receiving periphery of the roller, yat precise distances from frame-supported ends of an elongated coaxial support shaft. Such an anti-deflection roller is useful in any machine where bowing is to be avoided. The portions of the pressure-receiving sleeve and/ or support shaft between the bearings is of greater section modulus to inhibit bowing.

In a two-roller machine for rolling sheet metal where a first roller has a rigid periphery, means are provided for defining two relative positions for the rollers, the rst position with the rollers forced together and the second position fwith the rollers spaced apart, and means are provided for sequentially moving one of the two rollers between the two positions. Continuously adjust-able means are provided for selectively controlling the precise spacing between the centers of the rollers. The urethane rubber roller is arranged to be slid by force multiplying means along track ways between the sai-d two positions. One end of the rigid-periphery roller ymay be selectively freed sequentially from its support to afford removal of the sheet metal tube formed thereon. One or both of the rollers is preferably provided with anti-deflection character. Means are provided for accommodating flexing of the ends of the support shaft of the rigid-periphery roller. Rolling to different radii is accomplished by use of a tubular former positionedover the rigid-periphery roller.

This invention relates to a two-roll machine for rolling arcuate shapes substantially without at spots in the rolled shapes from metal sheet and plate, and more particularly this invention relates to a two-roll machine that is readily adjustable for selectively varying the pressure required to effect proper rolling of sheet or plate of different thick- In a co-pending application, Ser. No. 357,413, tiled Apr. 6, 1964, now U.S. Patent No. 3,304,757, there is disclosed a two-roller machine using a urethane rubber periphery on the driving roller for forming sheet metal without forming flat spots in the rolled shape. Insofar as there is common subject matter between this application for patent and said co-pending application, this application is claimed as a continuation-in-part of said co-pending application. This application discloses an improved machine for accomplishing rolling of shapes from metal sheet and plate, and wherein improved means are provided for readily selectively varying the pressure between the two rollers, so as to control the arcuate forming of the metal sheet or plate.

The rolling of sheet metal to obtain arcuate forms has been known for many years. Except for roll-type forming of very thin metal foils, in the range of thickness of .0005 inch or only slightly more, where the mere advancing of the foils around or against a hard tool or forming member causes the sheet to take a set leading to the easy forming of generally cylindrical shapes, or

where the metal foil because of its thinness or other characteristics very easily conforms to and practically adheres to the surface of a mandrel or roller being used to eect the forming of the sheet, the only machines, prior to the two-roller machines of these applications, for successfully rolling heavier sheet metal in gauge size and plate had required at least three rollers, such as in a pinch roll machine or in a pyramid roll machine.

With both pinch roll machines and pyramid roll machines, the metal sheet that has been rolled is not truly arcuate and the apparently arcuate shape actually comprises a series of distinct-flat segments that only tend to approximate an arcuate shape. The use of such three roller machines always produces ats Whose lengths are relatively long since they are a function of either the spacing between the points of tangency, between pairs of rollers where the three rolls have two pairs of tangents, or the spacing from the feed rollers to a deflecting roller. Many attempts have been made to correct the condition of liats obtained from such machines, but such attempts cause additional expenses and frequently do not fully correct the condition.

Another deficiency with three-roller machines is that the ends of the sheet are never properly subjected to the simultaneous bending action of all three rollers and, therefore, the ends are always relatively elongated ats which require special consideration.

In rolling metal sheet and plate of different thicknesses with a two-roller machine, the ability to properly bend the sheet or plate is a function of the pressure developed between the two rollers. In order for -a two-roller rolling machine to have desirably high utility, it must be readily selectively adjustable to vary the pressures obtainable between the two rollers over a wide range.

Where high pressures are developed at the bite between abutting rollers there is always the problem of bellying of one or both of the rollers, and there also exists the problem that rolled shapes of sheet metal would also belly to conform with a bellying pressure roller. It is, therefore, desirable to provide anti-deflection means for counteracting such deliection in the pressure rollers of a sheet metal rolling machine.

Where metal sheet or plate is being formed to a shape where the ends of the shape are spaced closer together than the width of the forming roller, there exists the problem of removing the fully formed shape from the forming machine. It is therefore desir-able to provide a metal forming machine of an improved construction for permitting withdrawal of the finished work from the metal forming machine.

Thus, one object of this invention is to provide an improved two-roller type machine for rolling metal sheet and plate.

Another object of this invention is to provide a tworoller type rolling machine having readily selectively adjustable means for varying the pressures developed between the two rollers.

A further object of this invention is to provide an improved anti-deflection construction for rollers that are subjected to uniform pressure loadings across the width thereof.

Still another object of this invention is to provide a metal forming machine that is equipped with improved means for permitting easy removal of the nished work from the forming machine.

Still a further object of this invention is to provide an improved two-roller type machine for rolling metal sheet and plate, which machine includes a combination, two or more of the improvements of adjustable means for varying the pressures developed between the two rollers, antideflection construction for the rollers, and means for effecting easy removal of the finished work from the forming machine.

Further objects and advantages of this invention will become apparent as the following description proceeds and the features of novelty which characterize this invention will be pointed out with particularity in the claims annexed to and forming part of this specification.

A preferred embodiment of the invention is shown in the accompanying drawing, in which:

FIG. 1 is a side elevational View, with portions broken away and in cross-section, of a machine constructed in accord with the inventions herein.

FIG. 2 is similar in some respects to FIG. l but shows the drop end in its open position and the pressurizing means in retracted position.

FIG. 3 is a reduced top plan view of the machine shown in FIG. 1.

FIG. 4 is an enlarged fragmentary cross-sectional View of the two rollers and a portion of the drop side of the machine of FIG. l.

FIG. 5 is a fragmentary cross-sectional View taken ou line 5 5 of FIG. 4.

FIG. 6 is a fragmentary cross-sectional view with parts broken away showing a portion of the selective adjustment means for varying the position of the first roller relative to the second roller.

FIG. 7 is another fragmentary vew of the adjustment means and is taken on line 7 7 of FIG 1.

FIG. 8 is a fragmentary view taken on line 8 8 of FIG. 6.

FIG. 9 is a perspective view of a modification showing use of a slip-on attachment for embossing patterns in light gauge metal sheets.

FIG. 10 is a perspective view of another modification showing use of a forming tube and support for forming metal sheet and plate to larger diameters with greater accuracy.

One of the important factors in being able to design the improved two-roller sheet metal rolling machine hereinafter described is the use of urethane rubber as the working surface of the driving roller of the machine. Urethane rubber, such as manufactured and sold by Du- Pont under the trademark Adiprene, has certain dedesirable charcteristics such as unusually high load bearing capacity, abrasion resistance, oil resistance and nonmarring. Under loadings from relatively rigid, non-deformable members, the extreme resiliency of urethane rubber permits it to temporarily deform to a precise shape corresponding to the shape of the deforming member, and furthermore, the non-compressible characteristic of the urethane rubber and its ability to perform like a confined hydraulic fluid exerting pressure substantially uniformly along its area of contact with a deforming member provides for attaining arcuity in bends not previously attainable with any other resilient or deformable material.

Referring now to the drawings there is shown in FIG. l a machine generally indicated at l@ that is adapted for rolling metal sheet or plate and is of the two-roller type. The machine 10 includes a frame generally indicated at 12, with a two-roller mechanism at the upper end of the frame for effecting rolling of the metal sheet or plate. Frame 12 includes a pair of laterally spaced uprights 14 and 16 joined together by lower cross-brace means 18 and an upper cross-brace means 20 in the form of a structural channel or the like. The rollers of the tworoller type sheet metal rolling machine include a first, or lower, roller means generally indicated at 22 and a second, or upper, roller means generally indicated at 24. The axis of the second roller means 24 is fixed with respect to the frame 12, while the axis of the first roller means 22 is movable toward and away from the second roller means through a mechanism that is hereinafter described. While the roller means 24, and the corresponding portion of roller means 22 could be of a solid construction throughout, in the instant machine these roller means have antideection character which will be understood from the description hereinafter.

The upright sides 14 and 16 of the frame are in the form of thick steel plates to provide requisite strength, and the upper ends of such sides 14 and 16 are vertically cut out, or channeled, respectively at 14a and 16a to dene spaced vertical parallel edges which form a part of a track means, as can be best seen by reference to FIG. 7. The cut outs 14a and 16a communicate at their lower ends with enlarged apertures or cutouts designated respectively at 14h and 16b. A heavy steel overlay, or bridging plate, 26 is provided on the outer side of upright 14 secured in position by means of a plurality of bolts 27, and a steel overlay or bridging plate 28 is similarly provided on the exterior of upright 16. The respective overlay plates 26 and 28 cooperate with the adjacent cutouts 14a and 16a, respectively, to define elongated guides or channels for receiving thereinto sliding support blocks associated with the first movable roller means 22 in a manner as hereinafter described. It will be observed that since the upright 14 extends to a greater height than does upright 16, that correspondingly the upper edge of bridging plate 28 terminates at a lower level than does the bridging plate 26. The plate 26 also carries thereon an axially elongated support block 30 rigidly secured t0 plate 26 by means of bolts 31 and the support block 30 being of a width to just fit between the spaced edges of the elongated cutout 14a.

The upright 14 also carries thereon a drive means that includes a motor 32 having a drive shaft 34 with a drive sheave means 36 thereon over which a belt means 38 is trained. The belt means 38 operates to drive a sheave means 40 carried on the input shaft 42 of a gear reducer 44. The output shaft 46 of the gear reducer extends through the upright support 14 and carries thereon a drive sprocket 48 which drives a chain 50 that is trained over a driven sprocket 52 which is operatively associated with the first roller means 22.

Mounted on the upright 16 is a drop-end means generally indicated at 54. The drop-end means 54 is movable between an operative position, seen in FIG. 1, and an inoperative position as seen in FIG. 2. The drop-end means includes an upright member 56 of channel-shaped crosssection that is pivoted at its lower end on a pin 58 that is carried on a support means 60 extending outwardly from the upright support 16. The upright support 16 also carries thereon sets of spaced guide ears or anges, including a set of upper ears 62 and a set of lower ears 64. The sets of guide ears or flanges are spaced, as best seen in FIG. 3, so as to closely receive therebetween the drop-end member 56 and to be in close association with the sides of member 56 so as to provide lateral support for the dropend member 56 when it is in the position of FIG. 1. The upper end of drop-end member 56 is enlarged or turned inwardly at 66 to provide better coperation with an end of the second roller means 24 in the manner as hereinafter described.

An actuator is provided for moving the drop-end means 54 between the positions of FIG. l and FIG. 2. The actuator means includes a fluid pressure cylinder 68 that is pivotably mounted intermediate its ends on a pair of spaced ears 70 to pivot about an axis 72. A lower portion of upright 16 is apertured at 74 to provide a recess through which one end of the cylinder 68 may swing. A piston 76 of the actuator extends outwardly of frame 16 and is pivotably connected by pin 78 to the drop-end member 56. Also mounted on upright 16 is a switch 80 that is normally spring biased outwardly and carries a movable actuator element 81 adapted to be engaged by finger 82 that is mounted on the web of the channelshaped drop-end member 56, so that when the drop-end member S6 is in the position of FIG. l, the finger 82 engages and moves actuator element 81 against its spring bias to an operative, or closed-switch, position, and when the drop-end member '56 is in the position of FIG. 2, then the actuator 81 of switch 80 is in its spring biased, or open-switch, position, as shown in FIG. 2. The linger 82 is screw adjustable to vary the point at which the actuator 81 is caused to be operative.

A second fluid pressure actuated means is provided for moving the lirst roller means 22 toward and away from the second roller means 24. This second fluid pressure actuated means includes spaced upright support-andguide bars 84 that depend from a Vrigid connection with the upper cross brace means 20, with the inner spaced upright edges of said guide bars 84 serving as track and guide means. A transverse support 86 is rigidly connected to the lower ends of the support bars 84. A fluid cylinder S8 is mounted on the transverse support 86. A fluid actuated plunger 90 extends upwardly from the fluid cylinand 16b respectively of the upright supports 14 and 16 slidably positioned between the spaced inner edges of the support bars 84 so that the actuator block 92 is in effect slidably mounted ina guideway betweenthe support bars 84.

Hollow gear boxes 94'are positioned in the recesses 14b and 16h respectively ofthe upright supports 14 and 16 and have portions thereof which extend laterally outwardly of the upright supports 14 and 16. The Width of the gear box 94 on upright 16 kis such that it tits between the legs of the channel-shaped drop-end member 56. Rigidifying braces 96 are provided for gear boxes 94 on the inside of the respective uprights 14-and 16.

Referring now to FIG. 4, there is shown in detail the construction of the first and second elongated roller means 22 and 24 that are carried by said frame, and a portion of the slide block construction which supports the movable first roller lmeans 22. The second roller means 24 is shown as including an elongated support shaft 100, a tubular elongated, relatively rigid, pressure sleeve 102, and a pair of spaced spherical bearings 104 which support the pressure sleeve 102 on the shaft 100. Support shaft 100 has outer ends 100:1 and 100b. The end 100:1 enters bore means 103 that is defined in plate 26 and support block 30 and which is slightly tapered or enlarged from its smallest size diameter so as to accommodate flexing of end `100a outwardly of the point of support for the shaft. A spacer hub on block 30, or washer, 105 is provided between support block 30 and the adjacent effective edge of the second roller means. The end 100b of the support shaft 100 carries thereon a journal block 106 whose shape is best seen in cross section in FIG. 5. The journal block 106 is shaped to provide a at upper side 106:1 and flat lateral side 106b, and the underside is unsupported thereby accommodating flexing of end 100b of the shaft. The upper extended end of drop-end member 56 and its enlargement 66 are recessed at 108 to dene a socket for receiving thereinto journal block 106. As best seen in FIG. 5, the socket 108 is lined to provide a top bearing plate 110 for engagement with the side 10651, and a pair of spaced side bearing plates 112 adapted for engagement with the flat sides 10619 of the journal block 106. The corners of the journal block 106 have been beveled or rounded so as to prevent interference with obtaining full bearing engagement with the top and sides of journal block 106 as is achieved oy the construction as seen in FIG. 5.

Turning now to the first roller means `22, said roller means comprises an elongated support shaft 110 which carries an elongated tubular sleeve 112 by means of a pair of spaced spherical bearings 114. The ends of support shaft 110 designated at l10n and 1101; respectively-are carried in slide blocks 116a and 116b which are arranged for sliding between the spaced upright edges of the recesses or cutouts 14a and 16a in the uprights 14 and 16 respectively. As can also be seen in FIG. 4, the outer surfaces of slide blocks 116a and 116b respectively engage the overlay or bridging plates 26 and 28 respectively carried by uprights 14 and 16. The ends of the support shaft 110 are rigidly secured by means of set screws 118e and 118b in bearing apertures provided in the slide blocks 116er and 116b. A sleeve of resiliently relatively deformable urethane rubber 120 is provided on pressure sleeve 112 for engaging the sheet metal to be formed by the mach-ine. The driven sprocket 52 is carried on one end of pressure sleeve 112 by means of a plurality of bolts 53 that screw into a anged portion 112a of the pressure sleeve 112. A portion of slide block 116a is laterally extended to provide a spacer sleeve 122 between block 116e and the adjacent edge of the first roller means 22.

The slide blocks 116a and 116b in which the ends of support shaft 110 are positioned, are part of the means for moving the rst roller means 22 toward and away from the second roller means 24. The details of the means for effecting movement of blocks 11611 and 116b are best shown in FIGS. 6 and 8, which disclose the details relating to block 116b and it being understood that similar construction relates to block 116a. As seen in FIG. 6, toggle link means are provided which includes the lower end of the elongated slide block 116b carrying a pin 124 upon which is pivotally connected a bell-crank type link 126. The lower end of link 126 is pivoted to a pin 128, while the shape of link 126 defines a crotch 130 for receiving and seating therein a pin 132. The pin 132 is carried by the free ends of a pair of spaced short levers 134 that are fulcrumed on a pivot pin 136. The pins 124 and 136 are located in vertically spaced, parallel alignment, with the upper pin 124 connected to and movable with slide block 1161; and with pin 136 connected to and movable with an eared abutment support member 142 hereinafter described.

The pin 128 is pivotally connected to the short levers 134 between the fulcrum 136 and the free ends of levers which carry the pin 132. The pin 132 is also connected to the outer ends of long levers 138, with the inner ends of levers 138 being pivotally connected on pins 140 to the actuator block 92. A pair of levers 138 are provided in association with each of the sli-de blocks 116a and 116i?, and the levers 138 of each pair are so spaced as to be located on opposite sides of the associate guide bar 84.

The fulcrum pin 136 is pivotally carried in an ear at the upper end of an abutment member 142 that is in the form of a shaft that is exteriorly screw-threaded to cooperate with screw threads on the inner bore of a nut-like driver 144 which is positioned within the hollow gear box 94. The nut-like driver 144 has a lower hub abutting the bottom wall of box 94 and a pinion gear 146 thereon in driven association with a worm gear 148 that is carried on a drive shaft means 150. Sections of the drive shaft means 150 are journalled in spaced side walls of each gear box 94 that is rigidly mounted in one of the frame uprights 14 or 16, and the sections are appropriately coupled together. The nut-like driver 144 is held axially in posi-tion in gear box 94 by a thrust washer 147. The gear box 94 is apertured at 142a and 142b to permit axial movement of the shaft-like member 142 through nut-like driver 144 and through the upper and lower walls of the gear box 94.

The drive shaft means 150 carries thereon a bevel gear 154 that is driven by a second bevel gear 156 as best seen in FIG. 8, which in turn is carried on an elongated cross shaft 158 that is appropriately journalled in other frame structure (159) and which is provided with a manually actuatable adjustment control in the form of hand-wheel 160 that is best seen in FIG. 1. It will be understood that the operator may rotate the hand-wheel 160 thereby causing rotation of the shaft means'150, and through the gear means effecting relative vertical movement of fulcrum 136 upwardly or downwardly relative to the gear box 94, so as to selectively vary the pressure that may be developed between` the roller means 22 and 24. The shaft means 150 is also drivingly connected by a positive drive, such as a chain 1-62, to indicia means in the form of a numerical counter 164 which serves to provide a read-out number value on the counter which can be coordinated with a precise location of the axes of fulcrum pins 136, depending upon the amount of rotation of shaft means 150 by the manual control wheel 160. Thereafter, by setting the read-out at a predetermined num-ber it will be possible to effect precise location of the axes of the shaft 136, so that it is possible to selectively duplicate the pressure being achieved between the roller means 22 and 24.

From the foregoing it will be seen that when the pressure cylinder 88 is actuated, by pressurized air or hydraulic pressure, to move the actuator 92 downwardly to the position of FIG. 2, the lever arms 138 also swing downwardly and thereby operate the toggle link means to pull the pin 132 inwardly away from the crotch 130 of the bell-crank arm 126, and this operates to swing the pivot pin 128 inwardly relative to the vertical line between the pins 124 and 136. This operates to move the articulated support, or toggle links, that exists between fulcrum 136 and pin 124 to an inoperative position and serves to release the rst roller means from its pressureapplying relation with the second roller means 24. On the other hand, when it is desired to impose a pressureapplying condition between the iirst and second roller means, the hand-crank 160 is first manipulated to a desired read-out on the counter 164, and then when the pressurizing cylinder 88 is pressurized by air pressure, or hydraulic pressure, whichever is used, the cylinder S8 operate to swing the long levers 138 upwardly to the position seen in FIG. l, and a tremendous mechanical advantage is obtained by the arrangement of levers. In the position of FIG. 1, the pin 132 swings into the crotch of the bell-crank shaped link 126 is a slightly over center position and this operates to lock the articulated supports, or toggle links, in their rigid locked position as seen in FIGS. 1 and 6, with the pin 124 at an extended relationship to fulcrurn 136, thereby forcing the slide block 116b upwardly to the selected position at which the urethane sleeve 120 is forced into the desired pressurizing relationship with the second roller means 24. This operates to impose a uniform loading of pressure along the entire length of contact between the urethane rubber sleeve 120 and the pressure sleeve 102 of the second roller means.

The machine is constructed to operate sequentially as follows. Since it is important that the second roller means be rigidly supported before any pressure is applied thereagainst from the rst roller means 22, the switch 80 is operatively associated with the pressurizing of cylinder 88 such that the cylinder 88 is not pressurized until the switch 80 has ben actuated by the plunger 82 carried by the drop-end means 54. The switch 80 is actuated only when the drop-end means 54 is swung to the position of FIG. l, in which positions the drop-end means operates as a retainer for roller means 24 to rigidly engage the free end of the second roller means 24. Thereafter the pressurized cylinder 88 is actuated to move the first `roller means 22 into pressurized engagement with the second roller means 24. Similiarly, in releasing the drop-end 54, there is a sequence of operations in which the pressurized cylinder 3S is first actuated to swing to the release position of FIG. 2 before the pressurizing cylinder 68 may be operated to swing the drop-end to the open position seen in FIG. 2.

When the drop-end 54 is in the inoperative position of FIG. 2, it has been swung in an arc about the axis of pin 58, the arc being located in a plane that is parallel to, or passes through, the axis of the second roller means 24, and this operates to render the one end of roller means 24 free so that a formed tube may be removed from the roller. In the extended position of drop-end 54, as seen in FIG. 2, the uppermost edge of the drop-end 54 is located spaced below the lower edge of the second roller means 24 so that removal of a cylinder of `formed steel or other metal can be effected by axial movement of the Cil CJt

formed part relative to the second roller means 24, and permitting clearance therebetween.

In the design of the roller means 22 and 24 to provide anti-deflection character, it will be seen that the construction of the support shaft and the pressurizing sleeve carried thereon by means of a pair of spherical bearings is substantially the same in both designs, so that discussion of the design of anti-deflection character in the second roller means 2d should be sufficient to fully explain the improvement features. The pressure sleeve 102 is shown in the form of a one piece member having a precise cylindrical exterior periphery. Considering that the portions of the sleeve 102 that extend outwardly of the spherical bearings 104 may be considered as end portions, the said end portions 102:1 are shown as being of uniform thickness and each of the end portions 102er has a section modulus that is no greater than the section modulus of the central portion of the sleeve member 102. In the preferred form, the central portion of the sleeve 102 is indicated at 102b, and said portion 10211 is of greater thickness than the end portions 102a, so that the section modulus of the central portion 10211 is preferably greater than the section modulus of the end portions 102a. Furthermore, the length of the thicker central portion 102b is so precisely selected that said portions define shoulders 102C against which the lateral edge of the outer race of the spherical bearing 104 abuts, so as to effect precise positioning of the bearings 104 from the terminal edges of the sleeve 102. In order to retain the inner races of the bearings 104 in position, the support shaft preferably has retainer sleeves 100e positioned thereon arranged for engagement with the inner race of the bearings 104. It will further be seen that the shaft 100 is preferably a one piece member and that an elongated portion of support shaft 100, that is located between the two bearings 104 and being designated between the lines 100d, is uniformly of greater thickness than the remainder of the support shaft, and this operates to further increase the section modulus of the assembly between the support bearings 104. The purpose of increasing the section modulus of both the sleeve 102 and the shaft 100 in the regions between the bearings 104 is for the purpose of further stiifening the central portion of the anti-deflection assembly, so as to resist the tendency of the roller means to belly, recognizing that the greatest chance for bellying occurs substantially midway between the supports for the sleeve portion of the roller means assembly.

Another important factor is the location of the center of each spherical roller means 104 precisely relative to the terminal ends of the sleeve 102. This point of location is determined by solving the following simultaneous equations:

In the foregoing equation, the symbols are as follows:

DM=deilection at the center of the sleeve DE=dellection at the terminal end of the sleeve W=uniform load E=modulus of elasticity for steel (3 X 107) I :moment of inertia of the section ITub=.0/+9 (D4-d4), where D is outer diameter and d is inner diameter C=distance from end tube to center of adjacent bearing l=distance between centers of spherical bearings L=length of tube In using machines constructed in accord with the following principles the deflection at the middle of the sleeve 102 has been maintained at less than .001 inch.

YIn solving the simultaneous equations, one sets DM=DE and upon solution one discovers that C2=.0494L2, while 12:.308L2. Thus, for all practical purposes,

N L N In the operation of the machine, it will be understood that roller means 22 is powered or driving, while the second roller means 24 is driven by relative movement of some body forced thereagainst. As a metal sheet or plate is introduced between the rollers, when they are in pressurized relationship, as seen in FIG. 1, the periphery of the urethane rubber sleeve 120 operates to engage the metal and to force the metal sheet through and past the bite between the roller means. The yielding pressure of sleeve 129 of roller means 22, which serves as a forming means, against the metal sheet and the corresponding pressure of the sheet against the relatively unyielding roller means 24 which serves as a former acts to roll the sheet into an arcuate form with relatively no flats, the arcuate form extending along the entire length of the sheet. The tightest arcuate shape which a sheet can achieve will tend to approach the radius of curvature of pressure sleeve 102. To obtain greater curvature in the sheet, additional force is required between roller means 22 and 2.4. The motor 32 which operates to drive the first roller means 22 is actuated by a manual control 17'() positioned on the front of the machine. When the manual control 170 is moved to its closed or operating position, then the drop-end 54 will first swing from its inoperative position of FIG. 2 to the operative position of FIG. 1, and then the first roller means 22 will be moved upwardly into pressurizing relationship with the second roller means 24.

In the form of device seen in FIG. 9, there is illustrated a slip-on attachment for the purpose of embossing patterns in light gauge metal sheets. The slip-on attachment is shown in the form of an embossing tube or cylinder 180 that is preferably hardened and has a pattern formed in the exterior4 surface thereof, and with the cylinder 18() freely slipped over the second roller means 24, so that a sheet of metal 182 as it passes through the machine engages the embossing surface on sleeve 180 and a pattern is formed or embossed in the light gauge metal sheet 182. The metal sheet 182 is caused to pass between the outer periphery of sleeve 180 and the sleeve 120 of urethane rubber.

In the form of device shown in FIG. l0, there is shown another modification that is used for forming with greater accuracy sheet into tubes of large diameter, or greater radius of curavature, than the diameter of the second roller means 24. As seen in FIG. l0, the forming tube or cylinder 190, having a precise dimension to which sheet 'metal is to be formed in a tube, is slipped over the second roller means 24 and is there held in position, with the lowermost portion of tube 190 tangently engaging the underside of the sleeve 102 of second roller means 24 and located between the roller means 22 and 24, by means of an elongated support arm 192 that is carried by upright 14 of the frame. The elongated support arm 192 extends substantially parallel to the axis of Said second roller means 24 and is spaced above said roller means 24. Adjustment means, such as screw threaded support 194, or slotted support 196 with clamping bolts 197 are provided to permit of adjustment of the support arm 192 to accommodate tubes 190 of greater or lesser diameter as required.

While there has been shown and described a particular embodiment of this invention, it will be obvious to those skilled in the art that various changes and modifications may be made therein without departing from the invention and, therefore, it is intended in the appended claims to cover all such changes and modifications as fall within the true spirit and scope of the invention.

What we claim as new and desire to secure by Letters Patent of the United States is:

1. A two-roller machine for rolling sheet metal comprising, in combination: a frame, first elongated roller means carried by said frame and providing a sheet metal engaging periphery of urethane rubber that is resiliently relatively deformable, second elongated roller means mounted on said frame and providing a relatively rigid periphery that is adapted to be rotated by relative movement of a metal sheet as it passes between said first and second roller means, drive means for selectively rotating said first roller means, said first roller means being slidably mounted on said frame for selective movement toward and away from said second roller means, and means for selectively moving said first roller means toward and away from the second roller means.

2. A device as set forth in claim 1 wherein the second elongated roller means has an end that may selectively be rendered free so that a formed tube of metal may be slid longitudinally of the second roller means to be removed from the machine, and a roller-means retainer carried by the frame for movement between an operative position at which it engages said free end of the second roller means and an inoperative position spaced from said free end of the second roller means.

3. A device as in claim 2 wherein the roller means retainer is pivoted to swing arcuately in a plane parallel to the axis of the second roller means.

4. A device as set forth in claim 1 wherein at least one of the roller means is provided with anti-detiection character achieved by means of an elongated support shaft supported at two spaced shaft-support points, a pair of sleeve-support bearings carried on the support shaft inwardly of said shaft-support points, an elongated pressure sleeve carried symmetrically on said sleeve-support bearings and serving as the operative surface of said roller means, and said sleeve-support bearings being positioned inwardly of the ends of the pressure sleeve a distance substantially according to 'the formula where vC is the spacing of a sleeve-support bearing from the closest end of the pressure sleeve and L is the length of the pressure sleeve.

5. A device as set forth in claim l wherein the means for selectively moving the rst roller means includes a manually actuatable adjustment control for effecting selective pressure control between said first and second rollers, and indicia means operatively associated with said manual adjustment control for providing a read out value that permits of selective duplication of desired pressure between said first and second roller means.

6. A device as set forth in claim 1 wherein the means for selectively moving the first roller means includes toggle link means which in one position locks the first roller* means in a pressure-applying relation to said second roller means and in a second position releases the first roller means from said one position.

7. A device as set forth in claim 6 including fluid pressure means for selectively moving the first roller means into and out of said first locking position.

8. A device as set forth in claim 1 wherein said first roller means is provided with articulated supports.

9. A device as set forth in claim 2 including fluid pressure means for selectively moving said roller-means retainer into operative position.

10. A device as in claim 2 wherein lock means are provided for selectively locking the first roller means in a pressure-applying relation with said second roller means or -for releasing the first roller means from said pressureapplying relation, and means for sequentially moving said roller-means retainer into its operative position and then mov-ing the lock means into pressure-applying relation with said first roller means to cause said device to be prepared for rolling sheet metal.

11. A device as in claim 1 in combination with an embossing tube of greater diameter than said second roller means, and which is fit over the second roller means.

12. A device as in claim 1 including means for increasing the accuracy of bend of sheet metal by the second roller means to radii larger than the radius of the second roller means.

13. A device as in claim 12 wherein said means for increasing accuracy includes an elongated support arm carried by said frame and extending substantially parallel to the axis of said second roller means and spaced from said second roller means, and a forming tube of greater diameter than said second roller means slid over and supported on said support arm and interposed between said first and second roller means.

14. In roller means of the type comprising an elongated pressure sleeve adapted to be uniformly loaded,

support shaft means coaxial of said pressure sleeve, and

two spherical bearings supporting said pressure sleeve concentrieaily on said support shaft means, the improvement of providing anti-deflection character to said roller means, comprising, the pressure sleeve defining end portions that are cantilevered outwardly relative to the two supports for said sleeve and a central portion extending between said two supports; said end portions being of uniform thickness and each having a section modulus that is no greater than the section moduus of the central portion, and positioning each of the two support bearings inwardly of the ends of the pressure sleeve a distance according to the formula C=L/4.5, where C is the axial spacing of the center of the bearing from the adjacent terminal end of the sleeve and L is the length of the sleeve.

15. A device as set forth in claim 14 wherein the central portion of the pressure sleeve along its length is uniformly thicker than the end portions of the pressure sleeve, so that the section modulus of the pressure sleeve is greatest between said support bearings.

16. A device as set forth in claim 15 wherein said thicker central portion of the pressure sleeve operates to assist in positioning the support bearings to accurately position said support bearings relative to the ends of the pressure sleeve.

17. A device as set forth in claim 15 wherein the pressure sleeve is a one piece member, the support shaft means is a one piece member, and an elongated portion of the support shaft located between the two support bearings is uniformly of greater thickness than the remainder of the support shaft, so as to increase the section modulus of the assembly between the support bearings.

18. A machine for forming sheet metal and readily permitting release of the formed part, comprising, in combination: a frame, forming means carried by said frame and providing a sheet metal engaging periphery, an elongated former mounted on said frame and providing a relatively rigid periphery that is adapted to be engaged by a metal sheet that is forced thereagainst, means for forcing said forming means toward said elongated former, the

elongated former having an end that may selectively be rendered free so that a formed metal shape may be slid longitudinally of the elongated former to be removed from the machine, and a retainer for said elongated formet' carried by the frame for arcuate movement in a plane parallel to the longitudinal axis of the elongated former and between an operative position at which it engages said free end of the elongated former and an inoperative position spaced from said free end of the elongated former.

19. A device as set forth in claim .1, wherein said second elongated roller means includes an elongated support shaft carried by said frame, and means providing for accommodation of flexing of the ends of said shaft under pressure applied to said second roller means by the first roller means being forced in a direction against said second roller means.

2th. A two-roller type sheet metal rolling machine for repetitious production `of rolled sheet metal parts comprising, in combination: a frame, a first roller means carried on said frame and providing a sheet metal engaging periphery of urethane rubber that is resiliently relatively deformable, a second elongated roller means carried on said frame and providing a relatively rigid periphery, drive means for rotating said first roller means, said pair of roller means having two positions relative to each other, the first being a pressurizing position in which a sheet of metal may be rolled to arcuate shape under pressure developed between the two roller means forced together, and the second position being with the rollers spaced apart to permit release of the rolled sheet metal from the rolling machine, and means operatively associated with one of the two roller means for sequentially moving said one roller of the two roller means into the first position where it is held during the forming of a sheet metal part and then moving the said one roller to the second position to permit release of the roller sheet metal part from the machine.

21. A device as in claim 20 where the means for sequentially moving the said one roller between first and second positions includes a force-multiplying means and a uid pressurized cylinder operatively associated with the force-multiplying means.

References Cited UNITED STATES PATENTS 355,390 l/l887 Daniels 72-238 2,454,282 11/1948 Johnson 72-169 2,662,573 12/1953 Cichoski 72-93 2,719,562 10/1955 Beegle 72-166 3,079,101 2/1963 Rockstrom 29-116 3,094,771 6/1963 Robertson 29-116 3,225,419 12/1965 Milton et al. 29-132 3,279,234 10/1966 Ames 72-465 3,293,728 12/1966 Hill 29-132 3,300,835 1/1967 Barr 29-132 CHARLES W. LANHAM, Primary Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,371,513 March 5, 1968 Howard S. Achler et a1.

It is certified that error appears in the above identified patent and that said Letters Patent are hereby corrected as shown below:

In the heading to the printed specification, line 2, "OPEN END ROLLING MACHINE" should read OPEN END ROLLING MACHINE AND ROLLERS HAVING ANTI-DEPLECTION CHARACTER Column 10, line 4Z, and Column 11, lne 32, each occurrence, should read s Column 12, line 37, "roller" should read rolled Signed and sealed this 14th day of October 1969.

(SEAL) Attest:

WILLIAM E. SCHUYLER, JR.

Edward M. Fletcher, J r. Attesting Officer Commissioner of Patents

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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3444716 *Jun 13, 1966May 20, 1969Calumet & HeclaDevice for bending,coiling,or straightening tubing
US3478555 *Dec 15, 1966Nov 18, 1969Kaufmann Tool & Eng CorpTwo-roll machine for rolling sheet metal
US3535903 *Jun 7, 1968Oct 27, 1970Tronchemics Research Inc Of CaRoll forming apparatus having rolls with radially and axially yieldable forming members
US3628360 *Jan 21, 1970Dec 21, 1971Niagara Machine & Tool WorksRoll forming machine
US3937052 *Jan 29, 1975Feb 10, 1976Mosstype CorporationMachine for rolling and curving printing plates
US5699740 *Jun 17, 1996Dec 23, 1997Creo Products Inc.Method of loading metal printing plates on a vacuum drum
CN102218459A *Jul 14, 2011Oct 19, 2011南通超力卷板机制造有限公司Numerical-control double-roll veneer reeling machine with adjustable rounding diameter
CN102218459BJul 14, 2011Oct 9, 2013南通超力卷板机制造有限公司Numerical-control double-roll veneer reeling machine with adjustable rounding diameter
DE3443851A1 *Nov 30, 1984Jun 5, 1986Kz Aviatsion Inst TupolevaZweiwalzen-blechbiegemaschine
DE19731050A1 *Jul 21, 1997Jan 28, 1999Creo Products IncMethod of loading metal lithographic printing plate onto cylinder or drum
DE19731050C2 *Jul 21, 1997Sep 2, 1999Creo Products IncVerfahren und Vorrichtung zum Anbringen einer Druckplatte auf einer Trommel oder einem Zylinder
WO2008116634A1 *Mar 26, 2008Oct 2, 2008Ttengineering S R LApparatus and method for bending of sheets for the manufacture of tubes
Classifications
U.S. Classification72/166, 100/162.00R, 492/2, 492/59, 72/54, 72/466
International ClassificationB21D5/14, B21D7/00, B21C37/08, B21D7/08, B21D5/00
Cooperative ClassificationB21D7/08, B21D5/14, B21D5/146
European ClassificationB21D5/14, B21D7/08, B21D5/14C
Legal Events
DateCodeEventDescription
Dec 19, 1986ASAssignment
Owner name: STRIPPIT-HOUDAILLE, INC., 12975 CLARENCE CENTER RO
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:STRIPPIT/DI-ACRO-HOUDAILLE, INC., A DE. CORP.;REEL/FRAME:004660/0022
Effective date: 19861208
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:STRIPPIT/DI-ACRO-HOUDAILLE, INC., A DE. CORP.;REEL/FRAME:4660/22
Owner name: STRIPPIT-HOUDAILLE, INC., A DE. CORP.,NEW YORK
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:STRIPPIT/DI-ACRO-HOUDAILLE, INC., A DE. CORP.;REEL/FRAME:004660/0022
Mar 29, 1985ASAssignment
Owner name: STRIPPIT/DI-ACRO - HOUDAILLE, INC. 12975 CLARENCE
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:HOUDILLE INDUSTRIES, INC., A CORP OF DE;REEL/FRAME:004381/0716
Effective date: 19850121