US3202006A

US3202006A - Rotating mechanism for plating barrel or the like

Info

Publication number: US3202006A
Application number: US293628A
Authority: US
Inventors: Jr Wendell G Lewellen
Original assignee: Imperial Industries Inc
Current assignee: Imperial Industries Inc
Priority date: 1963-07-09
Filing date: 1963-07-09
Publication date: 1965-08-24
Anticipated expiration: 1982-08-24

Description

24, 1965 w. G. LEWELLEN, JR 3,202,006

ROTATING MECHANISM FOR PLATING BARREL OR THE LIKE 2 Sheets-Sheet 2 Filed July 9, 1963 INVENTOR. WENDELL G. LEWELLE'N ATTORNEYS United States Patent 3,202,006 ROTATING MECHANISM FOR PLATHIG v BARRELOR THE LIKE Wendell G. Lewellen, In, Wayne, Mich., assignor to Imperial Industries, Inc., Wayne, Mich., a corporation of Michigan Filed July 9, 1963, Ser. No. 293,628 14 Claims. (Cl. 74-406) This invention relates generally to plating barrels of the type which are immersed and rotated at a relatively slow rate in plating baths during the process of plating articles contained Within the barrels. More specifically, the invention involves mechanism for rotating the barrels.

It is conventional to rotate a plating barrel by means of gearing formed of plastic or metal which is impervious to the effects of fluids used in plating baths. During the course of use, wear occurs at the bearings which support such a plating barrel, and this results in an increase in the distance between the centers of the plastic gears. This, in turn, causes the gears to mesh improperly and to wear at an increasing rate. Eventually, the resulting slack between the gears becomes so great that the gear teeth strike each other upon changes of loading on the gears, thereby breaking the teeth of one or more of the gears and requiring gear replacement. Moreover, conventional gearing cannot be conveniently disengaged to facilitate manual rotation of the plating barrel for convenient loading and unloading thereof.

. The primary object of the present invention is to provide a simple, inexpensive gear drive for a plating barrel improved so that it compensates automatically for wear at the bearings which support the plating barrel and for wear of the gear teeth themselves. Another object is to provide a gearing arrangement which facilitates convenient manual rotation of the plating barrel and which can be engaged with a gear on the barrel selectively at diiferent locations to meet the requirements of diiferent specific installations.

The invention generally contemplates the use of an idler gear between a drive gear and the driven gear on the barrel, the idler gear being mounted in such a way that it can move freely toward and away from drive transmitting relation between the drive and driven gears. The idler gear is held in mesh with the drive and driven gears by the forces which the latter two gears themselves exert 0n the idler gear. As wear occurs, the idler gear shifts automatically under these forces to take up the slack which would otherwise occur. One form of the invention is shown in the accompanying drawings:

FIG. 1 is a generally elevational view of a plating barrel utilizing a drive mechanism according to this invention, parts being broken away and shown in section to illustrate structural details.

FIG. 2 is an enlarged fragmentary generally sectional view on line 2-2 of FIG. 1.

FIG. 3 is a slightly enlarged fragmentary sectional view on line 33 of FIG. 2.

4 FIG. 4 is a fragmentary partly diagrammatic end view of the plating barrel and related parts.

' Shown in the drawings is a plating barrel rotatably supported within a plating tank 12 by means of two

hangers

14 and 16 having bearing connections to the ends of the barrel as at 18 and 20.

Hangers

14 and 16 are rockably attached respectively to horizontal supporting arms 22 and24, each of which carries adjacent its ends an electrode horn 26 supportedly engaged within recess blocks 28, anchored to top lip portions 30 of the plating tank. Barrel 10 is both supported and furnished electrical current through the electrode horns. A crosshead 32 is secured to the upper ends of

hangers

14, 16 to facilitate 3,202,086 Patented Aug. 24, 1965 raising and lowering of the barrel assembly relative to plating tank 12.

Barrel 10 has a removable top 34 through which workpieces are put into and removed from the barrel. barrel has holes 36 in its sides through which the plating bath fluids enter to contact the workpieces. Electrical current is conducted into the barrel from horns 26 by

cables

38 and 40, cables 40 extending downwardly through recesses in

hangers

14, 16 and into the barrel through hollow hubs at the ends of the barrel. Rocking of

support arms

22, 24 relative to the hangers facilitates leveling of the plating barrel despite incidental differences of vertical placement of blocks 28. Relative rocking of the support arms and hangers is limited by a lip 42 on each hanger spaced slightly above the top 44 of each support arm.

The drive for the plating barrel includes a large gear 46 non-rotatably fastened to one end of the plating barrel concentric with bearing connection 20. This gear is driven by a drive gear 48 through an idler gear 50. Gear 50 is mounted so that it can move freely toward and away from the interaxial line L between

gears

46 and 48. In the form of the invention illustrated, the mounting for gear 50 is an arm 52 provided with a collar 54 rockably surrounding a bushing 56 through which the drive shaft 58 for gear 48 passes. Arm 52 swings freely about the axis of drive gear 48. Hanger 16 and cross arm 24 are also secured to bushing 56 (FIG. 3) and a gear 60 is provided at the outer end of shaft 58. When the plating barrel assembly is in operative position on plating tank 12, gear 60 engages and is driven by another gear 62 rotated by suitable drive mechanism (not shown) which conventionally is permanently positioned adjacent the plating tank.

In a typical assembly, barrel 10, gear 46, and gear 50 are made of a plastic material, gear 46 being bolted to the barrel as represented at 64 (FIG. 2). The gear train is relatively inexpensive even though gear 46 is relatively large.

The axis of gear 50 is vertically intermediate the axes of

gears

46 and 50 and arm 52 extends at an oblique angle to the horizontal and vertical so that gear 50 tends by the force of gravity to remain engaged with gear 46. The interaxial line L between

gears

46 and 48 and the interaxial line L between

gears

48 and 50 define an included angle A; and this angle, measuring from the axis of gear 46 to the axis of gear 48 and then to the axis of gear 50, is opposite in direction to the direction of rotation of gear 48. Thus, in FIG. 2, assuming that gear 48 is rotating counterclockwise, angle A, measured in the direction indicated, is clockwise. Stated in another way, the axis of gear 50' is displaced laterally from the interaxial line between

gears

46 and 48 in a direction opposite to the direction of rotation of gear 48.

Gears

46, 48, and 50 are dimensioned and oriented so that the interaxial line L between

gears

46 and 50 is angled at preferably less than 45 to line L as shown in FIG. 2 for reasons given below.

In operation, it may again be assumed that gear 48 is rotating counterclockwise. Gear 46 resists rotation because of inherent frictional forces and inertia of the load carried by barrel 10. Gear 50 in turn resists rotation by gear 48. This results in the application of force by gear 48 tending to swing gear 50 in a counterclockwise direction as FIG. 2 is viewed. Moreover, the resistance of gear 46 to rotation results in a reactive'force on gear 50 which is tangential to

gears

46 and 50 where they interengage and whose direction is upwardly and to the right as represented by arrow F in FIG. 2. Since the angle between lines L and L is less than 45 the horizontal component of the latter force exceeds the vertical component and urges gear 50 counterclockwise.

The

' tween L 'and L Thus, the force of gravity and the component forces in the gear train itself maintain idler gear 50 in engage ment with gear 46. These forces are of sufficient mag nitude to eliminate the necessity of springs or other extraneous'mechanism for securing gears some 46 irri'nter-T shifts downwardly. 1 However, the forces acting on gear 50 during use cause it to swing counterclockwise to compensate for this shifting and maintain proper engagement with

gears

46 and 48. The same is true when wear occurs at the gear teeth themselves. all times. remains properly engaged despite these wear factors. Moreover, gear 50 is free to shift as required to compensate for any relative shifting of

gears

46 and 43 caused by-such other factors as thermalexpansion and contraction. I y

Barrel can be manually rotated in a counterclockwise direction as FIG. 2 is viewed to position its removable top 34 wherever desired to facilitate loading and unloading to the barrel. During this rotation of the bar Thus, the gearing at that theforce exerted on said idler gear by said 'driving gear, responsive tov inherent resistance to rotation by said barrel and driven gear, tends to supplement said bias, I p the interaxial line betweensaid idler and driven gears beingndisposed at an angle to that. between said driving and driven gears,

saidangles being so related that the radially outward component offforce exerted by said driven gear on said idler gear responsive to said resistance is insuffici'ent to overcome the combined eflects of said bias and' force supplementing said bias, a whereby said mount and idler geartend to shift toward said drive-transmitting relation'responsive to rotation of said ldriving' gear. t i 2. The combination defined in claim- 1 wherein said bias isgravitational.

( 3.The combination defin'ed in claim -2 wherein the latter-said angle is no greater' than 45 from the vertirel, idler gear 5%) merely bobs up and down in a ratchet- V t I mounting means includes an arm supporting said idler like action caused by the teeth on gear .46 pushing the teethon the idler gear out of the way. Subsequently,

whenthe barrel is driven by gear 48, idler gear 50 shifts counterclockwise asdescribed to take up'any slack. Alternatively, idler gear 50 canbe completely disengaged from gear 46 by swinging it upwardly; and this enables,

the barrel to be manually rotated in either direction. To re-engage the drive, gear 50 is merely swing down into engagement with gear 46. In the form of the invention illustrated, gear 50 remains engaged with gear 48 during cal. V t I 4. The combination defined in claim 2 wherein the latter-said angle is less than 45 fr'om'the vertical,

5. The combination defined in claim 1 wherein said gear in the general plane of said driving and driven gears, said arm being mounted for swinging movement to facili- 'tate' said relatively free movement of said idler gear toward'and awayfrom drive transmitting relation between said driving and driven gears.

F on gear 50 would be equal. lGravity and the counterclockwise force exerted on gear 50 by gear 48 would probably keep gear 50 engaged with gear 46. The; same might be true for angles. somewhat greater than be- However, it"is believedthat best results will be obtained where this angle is less than 45. 7

In a particular installation, it may be advantageous or necessary to mount idler gear in a position to the right of line L (dotted lines, FIG. 2) rather than to'thej left as shown in solid lines. This is accomplished during erec- 6. ,The combinationdefined in claim 5 wherein said arm is swingable selectively to'ang'ular positions on the oppositesides of the interaxial'line, between said driving and driven gears for selectively engaging said idler gear with said driven'gear at said angular position, whereby to facilitate utilization of said force on said idler gear 1 in either direction of rotation'of said driving gear.

' 7. .The combination defined in claim 5 wherein said arm is mounted for swinging movement substantially about 8. The combination defined'in claim 7 wherein said arm maintains said driving gear and idler gear continually in engagement. 7 7 .9. For plating and the like, a rotating barrel assembly having means which rotatably supports the barrel and tion of the plating barrel assembly merely by swinging arm 52 to the desired position. The onlyother requirement is that the direction of drive gear.48 be reversed. The force of gravityandthecomponent forces in the gear system will hold gear 50 in engagement with gear 46 in the manner described with the various directions being reversed. i v

Iclaim: p

e 1. For plating and the like, a rotating barrel assembly having means-which rotatably supports the barrel and having mechanism operable to rotate the barrel, 'saidjm'echanism comprising, 7 V

a driving gear and means operable to rotate said driving gear in one direction,

a driven gear carried by said barrel and having a driv ing relationthereto,

4 an idler gear and means movement toward and away fromdrive-transmitting relation between said driving and driven gears,-

said mounting means being jcOnstructedand arranged so that said idler gear is biased toward said drivetransmitting relation, 7 V v the interaxial line between said driving gear and idler gear in said "drive-transmitting relation being disposed, at' an angle to'the interaxial line between 'said driving gear and driven gear, said angle, measuredfrom the driven-gear axis to the driving gear axis and then to said idler gear axis, being opposite in direction to said one direction, so

mounting it for relatively free;

having mechanism operable to rotate the barrel, said mechanism'comprising,

\ a driving'gear and means operableto rotate said driving gear'in one direction, I a driven gear carried by saidbarrel and having a driving relation thereto, anidler gear supported :by anarmmounted for relatively free swinging movement substantially about the axis of said driving gear, said idler gear being engaged with said driving gearv and, responsive to swinging movementof said arm, being movable toward and away from drive-transmitting engagement with said driven gear, I a the axis of said idler gear being disposed above the axis of saiddriven gear and below the axis of said driving gear,.and said armand idler-gearbeing'grav- L i 'ity biased toward engagement by said idler gear with V, said driven gear, i t the interaxial. line between said driving gear and idler gear in said. drive-transmitting engagement being I disposed at. an angle to the interaxial line between said driving gear and driven gear, 7 i t saidangle, measured from the driven gear axis to the driving gear axis and then to said idler gear axis, being opposite'in direction to said one direction so that the force exerted on said idler gear by said driving gear responsive to inherent resistance to rotationbysaid barrel and driven gear supplements said 'gravitybias, the interaxial line between said idlerand driven gears being disposed atan angle of less than 45.. to the vertical so that the horizontal component of force exerted by said driven gear on said idler gear responsive to said resistance exceeds the vertical component thereof,

whereby said horizontal component supplements said force and gravity bias.

10. The combination defined in claim 9 wherein said idler gear is substantially free of forces tending to urge said idler gear into engagement with said driven gear other than said gravity bias and said forces exerted thereon by said driving and driven gears.

11. For plating and the like, a rotating barrel assembly having means which rotatably supports the barrel and having mechanism operable to rotate the barrel, said mechanism comprising,

a driving gear and means operable to rotate said driving gear in a predetermined direction,

a driven gear carried by said barrel and having a driving relation thereto,

an idler gear and means mounting it for relatively free movement toward and away from drive-transmitting relation between said driving and driven gears,

said mounting means being shiftable to engage said idler gear in said drive-transmitting relation selectively at two positions which are on opposite sides of the interaxial line between said driving and driven gears,

the direction of displacement of said idler gear from said interaxial line in each of said positions being opposite to said predetermined direction of rotation 0f said driving gear.

12. The combination defined in claim 11 wherein the axis of said idler gear in each of said positions is vertically intermediate the axes of said driving and driven gears and said idler gear is gravity biased toward said drivetransmitting relation, the interaxial line between said idler and driven gears being disposed at an angle to said interaxial line between said driving and driven gears within which the vertical component of force exerted by said driven gear on said idler gear responsive to inherent resistance of said driven gear to rotation is less than the horizontal component thereof so that said horizontal component supplements said gravity bias.

13. The combination defined in claim 11 wherein said mounting means comprises an arm mounted for swinging movement substantially about the axis of said driving gear, said idler gear being carried by said arm,

14. The combination defined in claim 13 wherein said means operable to rotate said driving gear includes a shaft on the support means for said barrel, said arm having a pivotal attachment around said shaft.

References Cited by the Examiner UNITED STATES PATENTS 829,068 8/06 Fox 74-354 879,616 2/08 'Eynon. 2,397,777 8/46 Colman 74409 DON A. WAIT E, Primary Examiner.

Claims

1. FOR PLATING AND THE LIKE, A ROTATING BARREL ASSEMBLY HAVING MEANS WHICH ROTATABLY SUPPORTS THE BARREL AND HAVING MECHANISM OPERABLE TO ROTATE THE BARREL, SAID MECHANISM COMPRISING, A DRIVING GEAR AND MEANS OPERABLE TO ROTATE SAID DRIVING GEAR IN ONE DIRECTION, A DRIVEN GEAR CARRIED BY SAID BARREL AND HAVING A DRIV ING RELATION THERETO, AN IDLER GEAR AND MEANS MOUNTING IT FOR RELATIVELY FREE MOVEMENT TOWARD AND AWAY FROM DRIVE-TRANSMITTING RELATION BETWEEN SAID DRIVING AND DRIVEN GEARS, SAID MOUNTING MEANS BEING CONSTRUCTED AND ARRANGED SO THAT SAID IDLER GEAR IS BIASED TOWARD SAID DRIETRANSMITTING RELATION, THE INTERAXIAL LINE BETWEEN SAID DRIVING GEAR AND IDLER GEAR IN SAID DRIE-TRANSMITTING RELATION BEING DISPOSED AT AN ANGLE TO THE INTERAXIAL LINE BETWEEN SAID DRIVING GEAR AND DRIVEN GEAR, SAID ANGLE, MEASURE FROM THE DRIVEN GEAR AXIS TO THE DRIVING GEAR AXIS AND THEN TO SAID IDLER GEAR AXIS, BEING OPPOSITE IN DIRECTION TO SAID ONE DIRECTION, SO THAT THE FORCE EXERTED ON SAID IDLER GEAR BY SAID DRIVING GEAR, RESPONSIVE TO INHERENT RESISTANCE TO ROTATION BY SAID BARREL AND DIVEN GEAR, TENDS TO SUPPLEMENT SAID BIAS, THE INTERAXIAL LINE BETWEEN SAID IDLER AND DRIVEN GEARS BEING DISPOSED AT AN ANGLE TO THAT BETWEEN SAID DRIVING AND DRIVEN GEARS, SAID ANGLES BEING SO RELATED THAT THE RADIALLY OUTWARD COMPONENT OF FORCE EXERTED BY SAID DRIVEN GEAR ON SAID IDLER GEAR RESPONSIVE TO SAID RESISTANCE IN INSUFFICIENT TO OVERCOME THE COMBINED EFFECTS OF SAID BIAS AND FORCE SUPPLEMENTING SAID BIAS, WHEREBY SAID MOUNT AND IDLER GEAR TEND TO SHIFT TOWARD SAID DRIVE-TRANSMITTING RELATION RESPONSIVE TO ROTATION OF SAID DRIVING GEAR.