US1728246A - Curvature-control mechanism for metal-forming machines - Google Patents

Description

C. MOREY Sept. 17,'19'29.

CURVATRE CONTROL MECHANISM FOR METAL FORMING MACHINES Filed Nov, 27, 1928 5 Sheets-Sheet C. MOREY sept. 17, 1929.

CURVATURE CONTROL MECHANISM FOR METAL FORMING MACHINES Filed Nov. 27, 1928 5 Sheets-Sheet 2 Sept. 17, 1929. c. MOREY 1,728,246

CURVATURE CONTROL MECHANISM FOR METAL FORMING MACHNES Filed Nov. 2'7, 1928 5 SheetS-Sheet 5 C. MOREY Sept. 17, 1929.

Filed Nov. 27, 1928 5 Sheets-Sheet 4 Swain. 17,41929.

c. MOREY y OURVATORE CONTROL MEOHANISM FOR METAL FORMINO MACHINES Filed Nov. 27, 1928 5 Sheets-Sheet 5 Patented Sept. 17, 1929 CARL MOR/EY, OF BIG RAPIDS, MICHIGAN CURVATURE-CONTROL MECHANISM FOR METAL-FORMING MACHINES Application filed November 27, 1528.

rIhis invention relates to an improvement in curvature-control mechanisms for metalforming machines, such as grinding machines and the like, and particularly to curvaturescontrol mechanisms for shaping crowned rolls for use in paper mills, metal rolling mills, etc., though not so limited.

Heretofore many feed-mechanisms have been devised for grinding or otherwise forming various crowned or concave surfaces, but these have all been more orv less inaccurate and have failed in particular to properly meet the requirements of shaping crowned rolls of the type above mentioned, since the nature of the curve of the crown usually desired corresponds substantially to the curvature of elasticity of the roll, or some other complex curve.

The object of this invention is to produce a superior curvature-control mechanism for grinding machines and other metal-forming machines of such character that complex curves may be accurately formed upon the work.

With this object in view, my invention consists in a curvature-control mechanism for metal-forming machines characterized by two complementary synchronized eccentric driving-members and means actuated by 3o both eccentrics for moving the cutter toward the work or vice versa, constructed and arranged in such manner as to cause the motion of one ofl the said eccentric drivingmembers to modify the motion of the complementary eccentric driving-member.

In the accompanying drawings:

Fig. 1 is a view in side elevation of a grinding machine embodying my improved curvature-control mechanism; n

Fig. 2 is a top or plan view thereof;

Fig. 3 is an end view thereof;

Fig. 4 is an enlarged-scale broken view in transverse section on the line 4 4. of Fig. 2;

F ig. 5 is a broken sectional view taken on 45 the line 5 5 of Fig. 4;

Fig. 6 is a similar but less comprehensive View taken on the line 6*(5 of Fig. e;

F ig. 7 is a detail sectional view on the line 7-7 of Fig. 1;

a0 Fig. 8 is an axial sectional view on the line Serial No. 322,138.

8-8 of Fig. 7 through one of the eccentric driving-units;

Fig. 9 is a diagrammatic view illustrating the action of one of the eccentric driving-r members in modifying the motion of its com- 55 plementary eccentric driving-meinber to produce a horizontal elliptical motion; and Fig. 1() is a corresponding view illustrating the eccentrics co-operating to produce a vertical elliptical motion. 6o t In the embodiment of my invention'her'ein shown, I employ a grinding-,wheel 15 or other suitable cutting instrument which I shall hereinafter refer to as the cutter.y This cutter is mounted upon one end 0f a shaft 65. 1G whichis mounted in spaced bearings 17 and 18 upstanding from any oscillating table or cutter-carrier 19 near the inner edge there-y of. The cutter-shaft 16 aforesaid y also mounts a pulley 2O which is positioned bee 70 tween the bearings 17 and 18 and has passing over it a belt 21 which also passes over the pulley 22 of an electric motor 23 mounted upon the upper face of the table 19 near the outer edge thereof. For maintaininer the belt 21 under suitable tension I provide an idler pulley 24 pressing` against the upper reach thereof and mounted'upon an inwardly and upwardly projecting arm 25 pivoted at its opposite end to a lug 26 upstanding from the S0 table 19. y y

The table 19 is mounted upon a transverse ly adjustable secondary-carriage 27 for oscillatory movement in a direction at a right angle to the axis of the roll 28. ,the periphery S5 of which latter it is intended to longitudinally curve, by providing the said table with flanges or skirts 29-29 respectively depend,- ing from its opposite sides and each formed near its inner end with a bearing-boss 30. In line with and spaced slightly inward from the bearing-boss 8O of the left-hand tableflange 29 I locate a short arm 31 depending from the underside of the top of the said gr table. Extending between the bearingbosses 30 and passing through the depending arm 81 is a trunnion-shaft 32 which also passes through a pair of arms 33 upstanding from the upper face of the secondary-car 100 riage 27 before mentioned near the respective opposite sides thereof, Y

rlhe secondary-carriage 27 is mounted upon a primary-carriage 34 for adjustment With respect thereto in a direction at a right angle to the aizis of the roll 28 by providing it upon its underface near its respective opposite sides with a depending V-shaped bearing-rib 35 and a iiat bearing-rib 36 sliding respective-ly upon tracks 37 and 38 formed in the upper face of the primary-carriage 34. yEhe adjustment of the secondary-carriage is effected by means of a long adjusting-screw 39 threaded at its inner end and passing through an internally-threaded lug 40 de- .pending from the underside of the secondrlhe outer end of the ad-l ary-carriage 27. justing-scre-W 39 is mounted for rotation in a lug 41Y upstanding from the primary-carriage 33 and in which it is held against axial movement by collars42-42 respectively located on the opposite sides of the lug 41.

` The primary-carriage 34 is mounted for movement in a. direction parallel with the airis of the roll 28 by securing to its underface a flat bearing-ribk 43 and a V-shapcd bearingrib 44 positioned respectively near its inner and outer eues. rlhe bearing-ribs 43 and 44 engage respectively With tivo parallel rails 45 and 46 coupled together by an integral ribbed web 47 and extending substantially throughout the entire length of the grinding machine parallel with the airis of the roll 28.

For the purpose of propelling the primarycarriage 34, together 'with the v secondarycarriage 27 and table 19 carried by it, length- Wise of the ` rails 45 and 46 above mentioned and therefore parallel with the axis of the roll 28, l secure to the Web 47 connecting the said rails a long horizontal rack 48 Whichis positioned ladjacent the track 46 parallel therewith and is secured in place to the said web 47 by means of bolts 49 (Fig. 4). Meshing into thesaid rack is va propeller-Worm 50 mounted upon the outer end of an'inclined propeller-shaft 51 mounted near its Vrespective opposite ends in bearings 52 and 53 formed in the rprimary-carriage 34. At the end opposite to the Worm 50vthe said propeller-shaftl has secured to it a Worm- Wheel 54 meshing into a Worm 55 upon'a transverse shaft 56'Which shaft also carries a bevel-gear 57 meshinginto a bevel-pinion 58 carried at the inner end of a. short horizontal shaft 59 which is driven by a motor 60 through connecting means, including sprocket-Wheels 61, 62, sprocket-chain 63, and a suitable change gear-set indicated at 64 in Fig. 5.

To rock the oscillating cutter-table 19 so aste cause the cutter 15 to movetoward and away from the roll 28 as the primary-carriage 34, secondary-carriage 27, table 19 and the said cutter are moved parallel With the axis of the said roll as above described, l provide a curvature-control mechanism consisting of tvvo complementary eccentrics 65 and 66 respectively embraced by links 67 and 68, each of which is forked at its upper end so as to nest together, as shown in Figs. 4 and 6, Where they are coupled together by means of a transverse-coupling pin 69 which mount-s a roller 70 positioned between the forked upper ends of the said links and bearing against a hardened thrust-plate 71 secured to the underface of the oscillating table 19 near the outer edge thereof.

The above-mentioned eccentrics 65 and 66 are respectively driven'through corresponding adjusting-mechanisms to be hereinafter described, by means of parallel drive- shafts 72 and 73 to the inner end of each of which is splined a Worm-Wheel 74, each of Which meshes into a Worm 75, one of Which is carried near the respective opposite ends of a short horizontal shaft 76 supported in arms 77 upstanding from the primary-carriage 34. The Worms 74 of the respective shafts 72 and 7 3 are positioned between the arms of a bifurcated bracket 78 opstanding from the primary-carriage 34 and providing a bearing for the respective inner ends of the said shafts 72 and 73. At its right-hand end the shaft 7 6 is provided With a gear 79 meshing into a gear 8O secured to the inclined propeller-shaft 51 before referred to, so that the eccentrics 65 and 66 are driven synchronously With the turning of the said shaft- 51 and hence at a predetermined ratio with respect to the longitudinal travel of the carriages 34, 27, table 19 and cutter 15.

The eccentrics 65-and 66 are each coupled to their respective drive- shafts 72 and 73 for rotary adjustment with respect thereto andwith respect to each other, by correspondino` mechanism, so that a description of one of such mechanisms will serve for both. For the purpose of description I have selected the mechanism connecting the eccentric 66 to its drive-shaft 7 3.

The eccentric 66 is secured to the inner end of a drive-sleeve 81 mounted upon the outer end of the drive-shaft 73 withy capacity for rotary adjustment thereon. The said sleeve 81 is mounted for rotation in a flanged tubular bearing-casting 82 secured in a recess 83 in the front face of the secondary-carriage 27 by means of bolts 84, and is formed at its outer end with a circular plate-like head 85 to the front face of which is secured, by means of bolts 86, an internal gear 87. Meshing into the said internal gear is an eccentrically-positioned pinion 88 secured to a short shaft 89 which has bearing near its inner end in a plate-like head 90 formed at the outer end of the drive-shaft 73. The outer end of the said shaft 89 bears in a plate 91 which complements the plate-like head 90 in form, so as to produce between them a gearchamber 92, the said head 90 and plate 91 being spaced apartby a spacer-ring 93 and secured together, so as to constitute asingle unit, by means of bolts 94.

Secured to the shaft 89 near the outer end thereof and between the head 90 and plate 91 is a worm-wheel 95 meshed into by a worm 96 at one end of a short shaft 97 tangentially positioned with respect to the shaft 89 andA carrying near its opposite end a spiral gear 98 meshing into a corresponding` gear 99 secured to an adjusting-shaft 100 which, as shown in F ig. 8 bears at its inner end in a bore 101, formed in the outer end of the drive-shaft 7 3, and at its outer end in a boss 102 in the plate 91 aforesaid. The tangential shaft 97 carrying the worm 96 and spiralgear 98 is positioned in the gear-chamber 92 and is supported in lugs 108 projecting forward from the head 90.

The adjusting-shaft 100 carries an adjustable dial-plate 10-1, the beveled periphery 105 of which is provided with calibrations which are adapted to be read in connection with suitable markings on the beveled periphery 106 of the plate 91. The dial-plate 1011 is sleeved over the outer end of the adjustingshaft 100 and is seated against an annular iiange 107 thereon by means of a kuur-led binding-wheel 108 internally-threaded for co-action with threads 109 formed near the outer end of the said shaft 100 which is also provided with a polygonal terminal 110 for the reception of an adjusting-wheel or handle. n

By turning the adjusting-shaft 100, the spiral-pear 99 thereon will rotate its complementary spiral-gear 98, thereby turning the shaft 97 and the worm 95, which latter in turn will rotate the worm-wheel 95, shaft 89,

pinion 88, internal gear 87 and through the latter which is secured to the plate-like head 85 of the sleeve 81 effect the rotation of the said sleeve and the eccentric 67 mounted upon the inner end of the said sleeve, so as to change its position with respect to its driveshaft 78 and hence with respect to the complementary eccentric 65. It will be understood that this adjustment of the eccentric is made while the machine is at rest, at which time both of the drive- shafts 72 and 73 are virtually locked against rotation by the worm-wheels 74 and worm 7 5.

lt will be seen from the foregoing that the eccentrics G6 and 67 may be rotated with respcct to their respective drive-shafts 72 and 7 and hence with respect to each other, so that their angular disposition with respect to each other may be varied as required and for the purpose as will hereinafter appear.

During the action of forming of the periphery of the roll 28, the same is slowly rotated by an electric motor 111 acting through a reduction-gear mechanism 112 of standard type, the drive-shaft 113 of which is connected by a pair of universal joints 114-114 and driving-collar 115 to the reduced end 116 of the said roll` The roll is suspended between two complementary vertically-adjustable pillow-blocks 117 which receive the reduced trunnions 118 of the said roll. Each of the pillow-blocks 117 is mounted upon a bedplate 119 which bears upon and spans the gap between two parallel longitudinal tracks 120 so as to be adjustable thereon to accommodate different lengths of rollers.

In ythe use of the roll-grinding machine above described, the primary-carriage, together with the secondary-carriage, table 19 and cutter 15, is shifted upon the rails l15 and 16, so that the said cutter is adjacent one end of the roll. By means of the adjusting-shafts 100, the angular inclination of the eccentrics and 66, one with respect to the other, are adjusted to a position to give the desired motion to the oscillating table 19 as may be required for the particular roll or other work being formed.

After suitable klateral adjustments of the secondary-carriage toward and away from the roll 28 have been made, the motor 60 is caused to rotate the inclined propeller-shaft 51 with the effect of moving the primarycarriage 34 in a direction parallel with the axis of the roll 28 and at the same time rotating the eccentrics so as to cause the links 67 and 58 to move the roller 70 in such direction and to such `degree as to slowly permit the cutter 15 to move outward from the axis of the said roll 28. The eccentrics are so po-l sitioned that when the cutter 15 reaches a point midway between the ends of the roll 28, the cutter will then start to move inward toward the axis ofthe said roll at a rate corresponding to its retirement during its travel from its opposite end to the center of the roll, so that the periphery of the said roll is crowned uniformly on each side of its midportion. Itis of course obvious that in many cases repeated grindings are necessary to produce the desired finish.

It will be noted that the travel of the cutter 15 in a direction substantially parallel with the axis of the roll is proportioned to the oscillatory movement of the table 18, since both movements are effected by means of the inclined shaft 51.

Should it be desired to form a. crown upon a roll having a different curve of elasticity, due to difference in diameter or length, the eccentrics may be adjusted by means of their adjusting-shafts 100 to cause the cutter to be retired and advanced with respect tothe periphery of the roll at a rate proportionate to its travel lengthwise of the said roll, corresponding to that required for the work in hand.

By adjusting the relative angular positions of the two eccentrics 65 and 66, the roller 70 may be caused to describe a practically infinite number of figures. In Figs. 9 and 10 of the drawings, I have schematically shown the eccentrics dierently positioned one with respect to the other so thatV in oneinstance they produce a verticalelliptical figure and in the other a horizontal elliptical figure.

While I have, both in the specification and claims, designated the two eccentrics as be ing synchronized7 I wish to have it understood that I employ that term in the sense thatboth eccentrics are concurrently driven. It will bel readily understood that the eccentrics may be driven at different rates of speed and in opposite directions, if desired, though I prefer to drive them at uniform speeds and in the same direction to facilitate the calculation of the resultant figure to be described by the roller and hence of the ratio of inward and outward movement of the cutter l5 to the longitudinal travel thereof.

I claim:

l. Thev combination with ak cutter, a cuttercarrier and a work-carrier; of a curvaturecontrol mechanism for causingrelative movement between thefsaid carriers in a direction substantially perpendicular to the surface of the work to be cut and comprising two complementary synchronized eccentric drivingmembers, means actuated by botlreccentrics and interposed between the same and one of the said carriers in such manner as to cause the motion of one of the said eccentric driving-members to modify the mot-ion of the com-v plementary eccentric driving-member in moving the said carrier through the said interposed means.

2. The structure defined in claim l in which adjustable connecting-means `is provided between the two eccentric driving-members for varying theirV relative angular positions whereby the edect of the motion of one eccentric in modifying the motion of its com alementary eccentric may be varied.

3. The structure defined in claim 1 in which adjustable self-locking worm and worm-gear connections are provided between the two eccentric driving-men'ibers for varying their relative angular positions whereby the effect of the motion of one eccentric in modifying the motion of its complementary eccentric may be varied.

il.. The combination with a cutter, a cuttercarrier and a work-carrier; of propelling means for moving one ofthe said carriers with respect to the other in a direction substantially parallel with the surface of the work to be cut; a curvature-control mechanism for causing relative movement between the said carriers in a direction substantially perpendicular to the surface of the work to be c ut and comprising two complementary synchroniZed eccentric driving-members, means actuated by both eccentrics and interposed between the same and one ofthe said carriers in suoli manner as to cause the motion of one of the said eccentric driving-members to modify the motion of the complementary eccentric driving-member in moving the said carrier.

5. The structure defined in claim l in which means is provided for interconnecting the propelling means and the feed-mechanism so as to maintain a predetermined relation between the action of both.

6. The combination with a cutter, an oscillating pivotal cutter-carrier and a work-carrier; of a curvature-controlmechanism for rocking the said pivotal cutter-carrier in a direction substantially perpendicular to the surface of the work to be cut and comprising two complementary synchronized eccentric driving-members; means actuated by both eccentric driving-members and interposed between the same and the said pivotal cuttercarrier in 'such manner as to cause the motion of one of said eccentric driving-members to modify the motion of the complementary eccentric driving-meinber in rocking the said pivotal cutter-carrier through the said interposed means.

7. The combination with a cutter, an oscillating pivotal cutter-carrier and a work-carrier; of propelling means for moving the said cutter-carrier in a direction substantially parallel with the surface of the work to be cut; a curvature-control'mechanism for rocking the said pivotal cutter-carrier in a direction substantially perpendicular to the surface of the said work and comprising two complementary synchronized eccentric drivingmembers; means actuated by both eccentric driving-members and interposed between the same and the said pivotal cutter-carrier in such manner as to cause the motion of one of said eccentric driving-members to modify the motion of the complementary eccentric driving-member in rocking the said `pivotal cutter-carrier through the said f, interposed means; and means interconnecting the said propelling means and the said feed-mechanism so as to maintain a predetermined relation between the action of both.

8. The combination with a cutter, a cuttercarrier anda work-carrier; of a curvaturecontrol mechanism for moving one of the said carriers with respect to the other in a direction substantially perpendicular to the surface of the work to be cut and comprising two complementary eccentric driving-members a pair of links respectively connected to each of the said eccentric driving-members and also connected together at their opposite ends; and means for synchronizing the movenient of the said eccentric driving-members; whereby the motion of one of the said eccentric driving-members in causing relative movement between thc said carriers is modified by the movement of the complementary eccentric driving-member.

9.y rlhe combination with a cutter, a cuttercarrier and a work-carrier; of propellingmeans for moving one of the said carriers with respect to the other in a direction substantially parallel with the surface of the work to be cut; a curvature-control mechanism for moving one of the said carriers with respect to the other in a direction substantially perpendicular to the surface of the said work and comprising two eccentric driving-members, a thrust-member, a pair of links respectively connected to each of the said eccentric driving-members and also connected together and to the said thrust-member at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members; whereby the motion ol one of the said eccentric driving-members in causing relative movement between the said carriers is modified by the movement of the complementary eccentric driving-inember.

l0. The combination with a cutter, a cutter-carrier and a work-carrier; of propellingmeans for moving one of the said carriers with respect to the other in a direction substantially parallel with the surface of the work to be cut; a curvature-control mechanism for moving one of the said carriers with respect to the other in a direction substantially perpendicular to the said work and comprising two eccentric driving-members, a pair oie links respectively connected to each ot the said eccentric driving-members and also connected together at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members with respect to each other and with respect,

to the said propelling-means; whereby the motion of one ot the said eccentric drivingmembers in causing relative movement between the said carriers is modified by the movement of the complementary eccentric driving-member and whereby a ratio ot' action is maintained between the propellingmeans and the feed-mechanism.

ll. The combination with a cutter, a movable cutter-carrier and a work-carrier; ot a curvature-control mechanism for moving the said cutter-carrier in a direction substantially' perpendicular to the surface of the work to be cut and comprising two complementary eccentric driving-members, a pair of links respectively connected to each of the said eccentric driving-members and also connected together at their opposite ends, and means for synchronizing the movement ol' said eccentric driving-members; whereby the motion of one of the said eccentric driving-members in moving the said cutter-carrier toward the work is modified by the movement ot the complementary eccentric driving-member.

l2. rilhe combination with a cutter, a movable cutter-carrier and a work-carrier; of propelling-means for moving one ot the said carriers with respect to the other' inr a direction substantially parallel with the surface of the work to be cut; a curvature-control mechanism for moving the said cutter-carrier in a direction substantially perpendicular to the surface of the work to be cut and comprising two complementary eccentric driving-members, a pair of links respectively connected to each of the said eccentric driving-members and also connected together at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members with respect to each other and with respect to the said propelling-means; whereby the motion of one of the said eccentric driving-members in moving the said cutter-carrier toward the work is modified by the movement of the complementaryeccentric driving-member and whereby a. ratio of action is maintained between the propelling-means and the feedmechanism.

13'. The combination with a cutter, an oscillating pivotal cutter-carrier and a Workcarrier, of a curvature-control mechanism for rocking the said pivotal cutter-carrier in a direction substantially perpendicular to the surface of the work to be cut and lcomprising two complementary eccentric driving-niembers, a pair ot links respectively connected to each of the said eccentric driving-members and also connected together at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members; whereby the motion of one of the said eccentric driving-members in rocking the said pivotal cutter-carrier is modified by the movement of the complementary eccentric drivingmember.

14, The combination with a cutter, an oscillating pivotal cutter-carrier and a workcarrier; of propelling-means for moving one of the said `carriers with respect to the other in a direction substantially parallel with the surface of the work to be cut; a curvaturecontrol mechanism for rocking the said pivotal cutter-carrier in a direction substantially perpendicular to the surface of the work to be cutand comprising two complementary eccentric driving-members, a pair of links respectively connected to each ot the said eccentric driving-members and also connected 'together at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members with respect to each other and with respect to the said propellingmoans; whereby the motion ot one of the said eccentric driving-members in rocking the said pivotal cutter-carrier is modified by the movement of the complementary eccentric driving-member and whereby a ratio of action is maintained between the propellingmeans and the feed-mechanism.

l5. The combination with a cutter, an osillating pivotal cutter-carrier mounted for bodily movement in a direction substantially at a right angle to its direction of oscillation and a work-carrier; of propelling means for moving the said cutter-carrier with respect i to the work-carrier in a direction substantially parallel with the surface oit the work to be out; a curvature-control mechanism for rocking the said pivot-al cutter-carrier in a direction substantially perpendicular to the surface of the work to be cut and comprising two complementary eccentric driving-members, a pair of links respectively connected to each of the said eccentric driving-inembers and also connected together at their opposite ends, and means for synchronizing the movement of the said eccentric driving-members with respect to each other and with respect to the said propelling-means; whereby the motion of one of the said eccentric driving-members in rocking the said pivotal cutter-carrier is modified by the movement or' the complementary eccentric driving-member.

16. The combination with a cutter, a cuttercarrier and a. work-carrier; of a curvaturecontrol mechanism for moving one of the said carriers with respect to the other in a direction substantially perpendicular to the surface oi' the work to be cut and comprising` two complementary eccentric driving-members, a pair of links respectively connected to each ofthe said eccentric driving-members and valso connected together at their opposite ends; and adjustable means interconnecting `the saideccentric driving-members for varying the relative angular positions of the same;

whereby the motion of one of the said eccentric driving-members in causing relative movement between the said carriers ismoditied by the movement of the complementary eccentric driving-member.

In testimony whereof, I have signed this specilication. f

' CARL MOR-EY.

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