US2670764A - Friction letoff for looms - Google Patents

Description

March 2, 1954 P. RANDALL ETAL FRICTION LETOFF FOR LOOMS 4 Sheets-Sheet 1 Filed April 17, 1952 LOUIS P RANDALL and MILES W SNIPES,

INVENTORS.

m we

ATTORNEYS.

March 2, 1954 L. P. RANDALL ET AL FRICTION LETOFF FOR LOOMS 4 Sheets-Sheet 2 Filed April 1'7. 1952 Lows P RANDALL and MILES W SNIPES,

INVENTORS.

ATTORNEYS March 1954 L. P. RANDALL ETAL 7 6 FRICTION LETOFF FOR LOOMS Filed April 17, 1952 4 Sheets-$heet 3 Lows P dPANDALL an Muzs W. SNIPEs.

BY 5am +M vINVENTORS.

ATTORNEYS.

L. P. RANDALL ET AL FRICTION LETOFF FOR LOOMS March 2, 1954 4 Sheets-Shae- 4 Filed April 17, 1952 1 9- LoulSagdRANDfll-L MILES W. 5mPEs.

INVENTORS.

BY 5034 .F M

ATTORNEYS.

UNITED STATErS FFIQE HUJZI N' LETO Q LO MS Louis P. Randall and Miles W, Snipes,

Lancaster; S

A p ica i n April 11 1952, s a No 2 1,82

15 Claims. (01. 139710? This invention relates to textile looms and, more especially, to an improved constant tension friction let-elf therefor.

There are at least two general types of let-off mechanisms in common use today high speed looms, which let-off mechanisms are commonly termed as positive let-offs and friction let-offs. As is well known, the positive let-offs of the Bartlett or the Roper types, employ positive actuating means acting through a braking mechanism to cause the warp beam to rotate and thus pay off the warp intermittently. However, the intermittent operation of the positive type of let-ofis has not been entirely satisfactory because they permit pericdic variations in tension of the warp yarns or threads which result in so-called thick and thin places in the woven cloth which results in wavy cloth and the production ofsecongls" with consequent loss to the textile mill operator.

The friction type let-01f has proven more satisfaetory since the warp is let offuniforrnly and constantly and therefore, it is the primary 0biect of this invention to provide a friction letoff mechanism which may be more simply constructed, installed and maintained thanfriction e -o fs h ret ore emp y d nd ich. i mo e efficient in maintaining uniform tension in the Wa yar s r h ads than f on t-ofi hi h e ur en y in re -v It a bj t f s nv n on to prov d an mrrov d fric i n l tf f l om wher in arp bee i pro ided w th a ge an a s eed eltir 'yi e seer s eo neeted to ee owar am ear and wherein a o or fri tion em n i riven by aid s eed mult ply ng ear the imrovern rrt in uding a stator rio iorr element restrained from rotation and means cqnt oliegi y variation in the diameter of t e Warp Wound n t e war-o been for varying the o e stator iriot on e ement aga nst the roto trioion element. sa d means eo n ri ine a first earn emb r adapted to m e wit a fo lowe arm rranged to be r the yarn on. the ere een. an said firs ea n membe he ri g a ainst a eeeor e can member ar on. a pre sure an er: g hearing against the. eorfaee of he sta or fr c ion el ment m te from. that faee whic e gages the rotor fr cti n element nd whereb relati e mo ement etwerr the nd econd 9am membe s causes pressur onplying mechanism to move relative to the rotor friction e ement tor torn. co tr l the pressur of the stator ir e element against the rotor friction element and of oorrir ng the.

tension in the warp yarns as they are paid off vide a friction let-off mechanism of the character last described with manually operable means for quickly releasing the pressure applying mechanism from engagement with the stator friction element to thereby permit an operator to rotate the warp beam Without being encumbored by the friction let-off mechanism, as may be desirablein the event of a smash, i. e., the I breaking of a plurality of the warp yarns at the fell of the cloth or for any one of many other reasons well known to those familiar with the art.

It is still another object of this invention to provide means for controlling the amount of tension effected by the friction let-off mechanism in the warp yarns relative to the friction effected between the rotor and stator friction elements by the first and second cam means heretofore described. other Words, a means is provided for varying the amount of pressure exerted by the pressure applying mechanism en the stator friction element although the first and second cam members are not moved relative t9 each th r Some of the objects of the invention having been stated ether objects will appear as the descripition proceeds when taken in connection with the aceompanying drawings, in which Figure 1 is a fragmentary side elevation of the rear portion oi the left-hand side of a loom sh qwing the improved friction let-off in assoiatior 'therewitr d o in the a le an? ember in ltern te Posit ons;

F ure an ele a ion, w th ar br ken, away, looki at. the l t-hand d o F u l and e r wine ooly the. port on o the o d a: cent the improved friction let-off mechanism;

Figure 3 a fragmentary sectional plan view looking down substantially along the line 3--3 in Figure '1;

Figure 4 is an enlarged fragmentary vertical sectional view, mostly in elevation, taken substantially along the line 44 in Figure 3;

Figure 5 is aview similar to Figure 4 but showret parts i a i e e pos io Figure 6 a vertical sectional view, mostly in levation. ta en eobet rrtiel l e e l 5+5 in Figu 1 with ar s b oke a a i ore 7 i errlere e ertieel eeei on l v ew ater; substan ally alon the li 1 in. igure 2 Figure 8 is a fragmentary top plan view of the structure shown in Figure 4;

Figure 9 is a vertical sectional view, on a reduced scale, taken substantially along the line 9-9 in Figure 7 and showing the rotor friction element in elevation;

Figure 10 (Sheet 2) is a fragmentary isometric view of the pressure applying disk and lever which are instrumental in effecting movement to the stator friction element and looking substantially along line lit-Ill in Figure 7.

Referring more specifically to the drawings, the numeral It! indicates the side frame member of a loom to which one end of a transverse frame member or girt I I is suitably secured, there being a side frame member similar to the frame member ID positioned at the other side of the 100m not shown, for supporting the other end of the girt ll. Each of the side frame members ID has a bracket I2 secured thereto which brackets support opposite ends of a shaft I3 of a warp beam I4 for rotation therein. The opposite ends of the warp beam I4 each has a disk or head i5 thereon and warp yarns Y are wound about the warp beam I4 between the disks I 5.

The warp yarns Y extend upwardly in Figure 1 from the warp beam I4 and pass over a guide roll or whip roll I6 supported for rotation in brackets I! which extend forwardly and are secured to a transverse whip roll shaft 20 oscillatably mounted in suitable brackets 2| secured to the side frame members ID of the loom. Although only a single one of each of the brackets I1 and 21 is shown, it is evident that similar brackets are disposed at the opposite side of the loom.

The yarns Y then pass forwardly from the whip roll l6 through the usual weaving instrumentalities, not shown, and then to a suitable takeup mechanism shown schematically at 23 in Figure 1. This take-up mechanism may be the usual sand roll of the loom. The disk or beam head I 5 has a relatively large gear 24 fixed thereon which meshes with a speed multiplying gear or pinion 25 fixed on the inner end of a let-01f shaft 26 which is a part of the improved friction let-off mechanism broadly designated at 27 and which will be later described in detail.

The shaft 26 is rotatably mounted in a let-01f shaft bracket 30 suitably secured to the inner surface of the side frame member l0, and also being suitably secured to the transverse frame member or girt H (Figure 2). A conventional beam lever or follower arm 33 bears against the warp on the warp beam M. This beam'lever 33 extends downwardly and the lower end thereof is fixed on one end of a beam lever shaft 34 oscillatably mounted in a beam lever bracket 35 suitably secured to the side frame member ID.

A suitable spring means is provided for normally urging the free end of the beam lever 33 against the warp wound about the warp beam I4 and, to this end, a beam lever spring in the form of a torsion spring 31 surrounds the shaft 34 and one end of the spring 3'! is secured to the bracket 35, the other end thereof being secured to the shaft 34. Collars 38, fixed on shaft 34, prevent endwise movement of shaft 34 relative to bracket 35. The parts heretofore described are conventional parts of the usual types of looms having a let-off mechanism associated therewith and it is with these parts that the improved friction let-off mechanism 2'! is adapted to be associated. The drawings show only a portion of a weaving loom since a description of the Willem-z '4 ing parts of the loom is not necessary for a complete understanding of the present invention.

The improved friction let-off 27 comprises a stator friction element 48 and a rotor friction element M. The stator and rotor friction elements ti! and 4! are shown in the form of disks, the stator friction disk 49 being provided with peripheral flange 42 which projects inwardly toward the frame member ID and loosely encircles the rotor friction disk 4| The rotor friction disk M is provided with a plurality of friction blocks 53 which project outwardly therefrom and frictionally engage the proximate surface of the stator friction disk 40.

The friction blocks 43 are preferably formed from cork or other friction material. It is to be understood that a disk of friction material may be secured to either the stator or rotor friction element 40 or 4! in lieu of the friction blocks 43, if desired. The rotor friction element 4| is suitably secured on the let-off shaft 25, as by a key 44 and a set screw 45, said set screw threadably penetrating the hub of the rotor friction element GI. element AI slidably and rotatably engages the outer surface of the bracket 30, which bracket loosely penetrates a suitable opening 46 in the side frame member II) of the loom.

The shaft it penetrates the hub of the stator friction element 46 for rotation relative thereto and the outer end of the shaft 26 also loosely penetrates a pressure applying disk 4! of a pressure applying mechanism designated broadly at 5E1 (Figures 2, 3, 6, '7, 8 and 10). The inner surface of the pressure applying disk 41 bears against the outer surface of the hub of the stator friction element or disk 40 as is clearly shown in Figures 3, 6 and '7. As best shown in Figures 1 and 10, the pressure applying mechanism 50 also comprises a pressure applying lever arm 5I provided with an enlarged annular portion 52 intermediate the ends thereof which loosely surrounds the pressure applying disk 41 and is provided with a pair of diametrically opposed grooves or slots 53 therein.

The pressure applying disk 41 has a pair ofdiametrically opposed projections 54 integral therewith which are preferably circular in crosssection and slidably penetrate the grooves or slots 53 in the annular portion 52 of the lever arm 5|. The lever arm 5| and the pressure applying disk t! may be integral, if desired. However, the lever arm 5I pivots about a vertical axis as it moves inwardly and outwardly rela tive to the shaft 26 and the present structure facilitates uniform engagement of the pressure.

applying disk 41 against the hub of the stator friction element 49.

The frame of the improved let-ofi mechanism 21 comprises a standard 60 (Figures 1, 2, 3, 4, 5, 6 and 8) on which the rear end of the pressure applying lever arm 5I may be pivotally mounted for pivotal movement about a vertical axis. However, a novel means is provided to permit pivotal movement of the rear end of the lever arm 5| which means facilitates adjustment of the corresponding end of the lever arm inwardly and outwardly relative to the rotor friction element 4| and which is quickly releasable to facilitate manual rotation of the warp beam I4 without being encumbered by the improved friction letoff 21.

To this end, it will be observed in Figures 41' and 5 that the upper end of the standard 60 spaced outwardly from the rear end of thepres-- Thus, the hub of the rotor frictionsource sure applying lever arm at and has a cavity M in the inner face thereof which is preferably polygonalin cross-sectionfor slidable reception of a plunger 62. The plunger 62- is engaged by an ad.- justment screw Gtwhich threadably penetrates the upper end of the standard 60- and a hand wheel 64 fixed on the outer end. thereof for ma nipulation by an operator. The screw 63 is; pro vided to vary the position of the plunger 62 relative to the standard. 60- for purposes! to.- be later described. A suitable lock nut 65- is tiri'eadably mounted on the screw 63 for locking the same in any desiredadjusted position.

'lhe bifurcated inner end of the plunger 6.2 hasa follower wheel or roller 65 rotatably mounted therein which ncrmally'engages'an eccentric cam 65. fixed: on a shaft 61 which is held against: the outer surface of the corresponding end of the lever arm at, in parallelrelation. to the longitudi-- nal axis thereof, by suitable bearing blocks It. The bearing blocks 'H} are suitably secured to the. outer surface of. the lever arm M: as by welding (Figure 8).

It will be observed in Figures 2 and 8' that; the shaft. 61 extends rearwardly' and: is bent at right angles to form a handle portion ll which. is adapted. to be manipulated by an operator for varying the position. of the eccentric cam 66; as shown in Figures 4 and. 5.. The lever: arm 5.1 is

provided with a cavity it to accommodate the cam 66' when it faces inwardly as shown in Figure 5. It will be noted that the cam as is provided with a notch; 13 in the periphery thereof and at the high point thereof, which notch $3 isadapted to be engaged by the follower wheel. 65 when the cam. 66' is in the position shown in. Figure: 4,, this being the normal operative position ofth-e cam 66 during operation of the improved friction letoff 21'.

It is thus seen that. the pressure applying lever arm 51 may pivot about a vertical axis relative to the follower wheel 65. The notch 13 the eccentric cam 66' is maintained in engagement with the roller or follower wheel 65 due to the pressure of the. rotorfriction element M against the stator friction element 4ft which pressure is transmitted to the cam 66 through the pressure applying mechanism 50;

The front portion of the pressure app-lying lever arm 5! normally bears against the lower surface of the horizontal leg of an inverted substantially L-shaped' gauge member or guide M cFigures 1, 2, 3 and 6'). The gauge member 7% is provided to assist an operator in properly positioning the lever 5! when it isinstalled asshown in thedrawings. The front end of the lever arm 5-6, that is, the end remote from the eccentric cam 65, has a longitudinally extending cam member F5 (Figures 1, 3, 6 and 7) suitably secured thereto or which may be an integral part thereof. The front portion of the cam i5 is substantially thicker than the rear portion thereof, as is clearly shown Figures 3 and '7, so the outer surface of the rear end of the cam 75 adjacent the disks 4'0, M is positioned closer to the disks than the front end of the cam 15 in planes parallel to the axis of the" surface of an auxiliary cam follower arm 83 (Figures 1, 2, 3, 6 and 7). g

The cam follower arm 80 extends downwardly and is fixed on the outer end of the beam fever shaft 34 heretofore described. The frame to which the lower ends of the standard 6.0: andthe gauge member M are secured may be of east con-- struction, desired. However, in this instance,

the frame comprises a pair of. lateral frame mom-- hers 82 and 83, the outer ends ofwhich are suitably secured to the respective rear and front ends of a bridging frame member 84. I

The frame member 83 extends: inwardly and isthen-bent upwardly and is suitably secured. to the sideframe member H The frame member 82- also extends. inwardly and is then bent upwardly and suitably secured to the frame member to. Flowever, this frame member: is also bent outwardly at its upper end then downwardly, as at. 9t (Figured) to serve as a support for an. upper restrai-n inga-rm 9i suitably secured thereto,; as by a screw- 92. The outer end of an angularly disposed bra-c?- ing member- 93. is suitably secured to the lower surface of the member 82,. this. bracing member 93 extending downwardly and inwardly and be ing suitably secured at its lower end to the sideframe member 1 0 lower restraining member 34 is suitably secured intermediate the ends of the lower horizontal portion of the frame member 82. and the friction disk 40 longitudinally of the shaft 26 and relative to the restraining members 9t at. I

It is thus seen that the restraining members 9! and 9% restrain the stator friction element or'di-s-kfrom rotation. Although theenlarged annular portion 52' (Figures 1 and 10) of the lever arm 5!. loosely surrounds the pressure applying disk 4%,. the lever Si is held inthe position shown due to;

the pressure between the stator friction element- Ml and the cam 'Hiand the cam 65 (Figures 1, 4,.-

5, '7 and 8) In operation, the pressure of the stator friction element-41f against the friction blocks 43 on the rotor: friction element 4!: gradually decreases as the diameter of the warp wound about the warp beam f5 decreases because of the outer surface of the front ends of the cam member 15 being spaced further from the disks 4b, 4! than the outer surface of the front end thereof and, of

course, when the warp on the warp beam H is. of relatively large diameter. As the warp yarns.

Y are paid off of the warpheam [-4, the diameter of the warp decreases whereupon the torsion spring, 31: (Figures 3 and. 6) causes thebeam lever 33 to move in a counter-clockwise direction in Figure 1, moving the auxiliary follower arm accordingly.

Since the outer surface of: the cam: 15 nearest the shaft 26 is spaced closer to the rotor frictionelement 4| than the outer surface of the remote or free end of the cam l5, this gradually relaxes the pressure of the statorfriction element 40 against the rotor friction element 4-! thereby insuring that the yarn-s Y are maintained under a constant uniform tension regardless of the diam.-- eter of the warp wound about the warp beam M."

It occasionally becomes necessary for an open" ator to rotate the warp beam 4' in either direc tion, such as: when replacing an empty warp beam with a filled warp beam. or for various other rea-' sons and, imorder that the operator is not'eni-z cumbered by the friction let-oft mechanism, it is merely necessary for the operator to grasp the handle portion 1| and to rotate the shaft 51 to move the cam 66 from the position shown in Figure 4 to the position shown in Figure 5. This will simultaneously permit the pressure applying mechanism 50 to move outwardly relative to the friction disks 40, 4| and thereby permit free rotation of the rotor friction element 4| and the let-01f shaft 26. After the operator has rotated the warp beam M as desired, the lever arm 5| is held in the proper position relative to the pressure applying disk 41 as the cam 66 is returned to the position shown in Figure 4 to again cause the stator friction element 40 to bear against the friction blocks 43 on the rotor friction element 4|.

As is well known, the tension required in the yarns Y varies with different types of yarns, the amount of twist in the yarns and the type of cloth into which the yarns are to be woven. Accordingly, the tension in the yarns Y may be varied relative to a particular diameter of the warp on the warp beam without changing the position of the follower 16 on the cam follower arm 80 relative to the cam 15 by adjusting the adjustment screw 63 in the manner heretofore described (Figures 1, 4 and 5). It is evident that this varies the amount of pressure exerted on the disk 40 by the pressure applying mechanism 50 (Figure relative to the follower 16 (Figures 3, 6 and 7) on the arm 80 being in engagement with a given point on the cam 15. The peripheral flange 42 (Figure '7) on the stator friction element or disk 40 serves to shield the friction blocks 43 from lint and other foreign matter.

It is thus seen that we have provided an improved friction left-off mechanism of simple construction with resultant economy in producing and maintaining the same and wherein means are provided for compensating for the decrease in diameter of the warp on the warp beam by accurately varying the pressure between the friction surfaces of the let-01f mechanism. Moreover, a means is provided to adjust the pressure between the friction surfaces of the let-off mechanism so the tension in the warp yarns may be varied relative to a given diameter of the warp on the warp beam. It is also evident that the pressure between the friction surfaces of the letoff mechanism may be quickly released to facilitate manual rotation of the warp beam or to relieve the tension in the warp yarns during periods in which the loom may not be in operation thereby assisting in preventing the occurrence of "set-mar in the woven cloth.

In the drawings and specification, there has been set forth a preferred embodiment of the invention and, although specific terms are employed, they are used in a generic and descriptive sense only, and not for purposes of limitation, the scope of the invention being defined in the claims.

We claim:

1. In a loom having a rotatable warp beam provided with warp threads wound thereon, an improved friction let-off comprising a first friction disk, a driving connection between the warp beam and said first friction disk for imparting rotation to the first friction disk, a second friction disk restrained from rotation and frictionally engaging said first friction disk and cam controlled means responsive to variations in the diameter of the warp on the warp beam for maintaining said friction disks in pressure engage- 8 ment and for, accordingly, varying the pressure of the friction disks relative to each other.

2. In a loom having a rotatable warp beam provided with warp wound thereon, a friction letoff mechanism having its input end connected to said warp beam, a stationary element and a rotary element connected to the output end of said mechanism and having juxtaposed surfaces in sliding engagement, a manually movable cam means normally applying pressure to said elements, adjustable means normally engaging said cam means and causing said cam means to apply pressure to said elements, means controlled by the diameter of the warp on the warp beam and co-acting with said cam means to reduce thepressure applied to said elements as said diameter reduces, and said cam means being movable out of engagement with the adjustable means to quickly release the pressure on the friction elements relative to each other and to thereby facilitate free rotational movement of the warp beam.

3. An improved friction let-off for a loom haying a rotatable warp beam provided with Warp wound thereon, a gear on said warp beam and a gear connected to said warp beam gear, said friction let-off mechanism comprising a first friction disk rotatable by said gear connected to the warp beam gear, a second friction disk restrained from rotation and frictionally engaging said first friction disk, a pressure applying mechanism movable axially against at least one of said friction disks for maintaining the said friction disks in pressure engagement, and cam actuated means controlled by the diameter of the warp on the warp beam for moving said pressure applying mechanism axially of the friction mechanism to vary the pressure exerted by the pressure applying disk on the corresponding friction element and to thereby maintain the warp under constant and uniform tension as the diameter of the warp on the warp beam decreases.

4. In a loom having a rotatable warp beam provided with warp wound thereon, the combination of a first rotatable friction element, mechanical connections between the warp beam and the first friction element for imparting rotation from the warp beam to the first friction element, a second friction element restrained from rotation and frictionally engaging said rotatable friction element, an axially movable pressure applying mechanism for maintaining said friction elements in pressure engagement, cam means carried by the pressure applying mechanism, and movable means movable in response to variations in the diameter of the warp on the warp beam and engaging said cam means on the pressure applying mechanism to cause axial movement of the pressure applying mechanism to thereby vary the pressure exerted by the pressure applying mechanism on the friction elements according to the diameter of the Warp on the warp beam and to maintain the warp under constant and uniform tension as the diameter of the warp beam decreases.

5. In a loom having a rotatable warp beam provided with warp wound thereon, the combination of a rotatable friction element, means operatively connecting said warp beam to said friction element for causing said friction element to rotate in proportion to the speed of said warp beam, a friction element movable axially into pressure engagement with said rotatable friction element, a pressure applying mechanism for pressing said axially movable friction element into engagement with the rofor pressing said axially movable friction element into engagement with the rotatable friction element and including a lever, a cam on one end of said lever, follower means engaging said cam to press the pressure applying mechanism into engagement with the axially movable element, means controlled by the diameter of the warp on the warp beam for moving said follower means relative to the cam, said cam being of such configuration as to cause axial movement of the pressure applying mechanism and the axially movable friction element in a direction to decrease the pressure effected by the pressure applying mechanism on the axially movable frictionelement as the diameter of the Warp on the warp beam decreases, means to lock said pressure applying mechanism in pressure applying position while said follower means is in engagement with said cam, and manually operable means to move said locking means to inoperative position to release the pressure applying mechanism from pressure applying position to thereby facilitate free rotation of the warp beam and the rotatable friction element.

12. In a structure according to claim 11, means to adjust said locking means relative to the axially movable friction element to vary the pressure efiected by the pressure applying mechanism relative to the pressure exerted thereon by the follower means engaging said cam.

13. In a loom having a rotatable warp beam provided with warp wound thereon; the combination of a rotatable friction disk, a driving connection between the warp beam and the rotatable friction disk for imparting rotation from the warp beam to said disk, an axially movable friction disk restrained from rotation and frictionally engaging said rotatable friction disk, a pressure applying mechanism for pressing said axially movable friction disk into engagement with the rotatable friction disk including a lever disposed outwardly of and extending transversely relative to said axially movable friction disk, means pivotally supporting one end of said lever to one side of the axis of the axially movable friction disk and being so arranged as to permit movement of said lever toward and away from the axially movable friction disk, means carried by the medial portion of said lever for pressing against the axially movable friction disk, a cam on the other end of said lever, follower means engaging said cam, means controlled by the diameter f the warp on the warp beam for moving said follower means relative to the cam, and said cam being so configured as to cause axial movement of the pressure applying mechanism and the axially movable friction disk in a direction to decrease the pressure effected by the pressure applying mechanism on the axially movable friction disk as the diameter of the warp on the warp beam decreases.

14. In a structure according to claim 13 wherein said loom has a shaft disposed in spaced substantially parallel relationship to the axis of said friction disks and a beam lever fixed on said shaft and bearing against the warp on said warp beam, said cam being in the form of an elongated member carried by and extending substantially parallel to the portion of said first-named lever remote from the pivoted end thereof, the outer surface of said elongated member being tapered relative to the axially movable friction disk so that one end of the elongated member is disposed further from the axially movable friction disk than the other end thereof, and said follower means including an arm fixed on said shaft and having means thereon engageable with the outer surface of said elongated member carried by the firstnamed lever.

15. In a structure according to claim 13, said means pivotally supporting one end of said lever including a manually rotatable eccentric cam carried by said lever and having a notch in the high point of the periphery thereof, said eccentric cam being mounted on an axis substantially perpendicular to the axis of said disks, a stationary standard spaced outwardly from said eccentric cam relative to the axially movable friction disk, a plunger mounted in said standard for adjustment parallel to axis of said disks, and having means thereon normally engaging the notch in said eccentric cam whereby said lever may pivot at the juncture of the cam with said means carried by the plunger, and whereby manual rotation of said eccentric cam will permit, the pivoted end of said lever to move outwardly relative to the first rotatable friction disk to release the axially movable friction disk from pressure engagement with the rotatable friction disk.

LOUIS P. RANDALL. MILES W. SNIPES.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 43,338 Reynolds June 28, 1864 62,369 Saunders Feb. 26, 1867 117,768 Graichen Aug. 8, 1871 503,462 Emery Aug. 15, 1893 1,466,100 Northrop Aug. 28, 1923 2,135,098 Bodie Nov. 1, 1938

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