US2268414A - Sewing machine - Google Patents

Description

INVENTOR les Meyer ATTORNEY Dec. 30, 1941. c. MEYER SEWING MACHINE Filed Nov. 2l, 1959 Ov @3 00 W sa, Z .t

Dec. 30, 1941. .Q MEYER 2,268,414

SEWING MACHINE F'iled NOV'. 2l, 1959 3 Sheets-Sheet 2 INVENTOR ATTO IEY Dec. 3o,v 1941. QMYR 2,268,414

SEWING MACHINE l Filed NOV. 2l, 19.39 Y 3 Shee'bS-Sheet 3 INVENTOR BYW V.

ATTORNEY Patented Dec. 30, 1941 SEWING MACHINE Charles Meyer, Yonkers, N. Y., assigner to Bartmann & Bixer Inc., New York, N. Y., a corporation of New York Application November 21, 1939, Serial No. 395,415

2 Claims.

This invention relates to sewing machines, particularly of the type adapted to perform hemming operations as in the manufacture of curtains, this being an improvement over my invention described in my Letters Patent #2,170,948, granted August 29, 1939.

It is a well known fact that during the usual hemming operation on curtains, especially those of celanese or similar material, a gathering or warping of the hemmed edge is produced, which cannot be satisfactorily flattened out even by a thorough pressing or ironing thereof. This is generally due to the fact that each stitch during the sewing operation puckers the material slightly, conventional machines not having any instrumentality to prevent such a puckering, a condition which has the effect of producing a rather considerable cumulative gathering throughout the length of the hem. It is primarily within the contemplation of my invention to overcome this shortcoming by enabling material, particularly curtains and the like, to be hemmed at the edges without any resulting gathering or puckering effect, whereby the finished product will be perfectly fiat and unwarped. This I accomplish in my invention by employing a system of rollers located behind the conventional feed dog mechanism, the rollers and the feed dog both being operatively synchronized in accordance with a predetermined setting, and being adapted to coact with the feed dog for effecting periodic tensioning pulls of the material during the sewing operation. In this manner a tensioning pull is applied not only to the material but also to the thread used in sewing, whereby the puckering or gathering in of the material by the thread is obviated.

In the mechanical embodiment of my invention, a certain tension is, as aforesaid, induced in the material during the sewing operation, an additional objective of this aspect of my invention being the provision of means for varying the tension or pull applied to the material, in accordance with the best practice for different kinds of fabric. I accomplish this result by a mechanism which enables a variation to be effected in the magnitude of feeding pull applied by the roller to the material as it is held between the presser foot and the feed dog or needle plate.

It is further within the contemplation of this invention to improve the structure of said Patent No. 2,170,948 by enabling the tensioning rollers to be operatively actuated either before, during or after the operative feeding movement of the conventional feed dog mechanism, thereby rendering this device adaptable for use with materials of different properties. This objective I accomplish by enabling the intermittent rolleractuating means to be operatively set in selected timed relation with respect to the main drive shaft.

And it is a further object of this invention to enable the aforementioned timing of the roller tensioning means to be eifectuated without affecting the peripheral speed of the rollers.

It is also an object of this invention to further improve the structure of said Patent No. 2,170,948 by providing a braking action upon the tensioning rollers to prevent their momentum from carrying them beyond the intended limits of rotation, thereby obviating the danger of excessive strains within the curtain material.

Other objects, features and advantages will appear from the drawings and the description hereinafter given.

In the drawings,

Figure 1 is a side elevation of a sewing machine containing my invention.

Figure' 2 is a fragmentary bottom View of Figure 1.

`Figure 3 is a front elevation of the sewing machine of Figures 1 and 2.

Figure 4 is a partial sectional plan of Figure 3 taken along line 4 4.

Figure 5 is a partial section taken along line 5--5 of Figure 4 showing the eccentric and clutch means employed in my invention.

Figure 6 is an enlarged fragmentary perspective of the adjustable eccentric means of Figure 5.

Figure 7 is a fragmentary side elevation of a portion ofy a sewing machine containing a modified arrangement of adjustable eccentric means for actuating the rollers.

Figure 8 is a section of Figure 7 taken substantially along line 8-8 thereof.

Figure 9 is a side elevation of a portion of the sewing machine of my invention showing an automatic braking device associated with the rollers, and

Figure 10 is a fragmentary section of Figure 9 taken along line Ill-l0,

In the drawings, the body structure l is of conventional sewing machine design, containing a head portion Il containing the usual needleactuating mechanism operatively connected in conventional manner to the pulley l2 which in turn is driven by the belt I3 connected to a transmission mechanism or other conventional driving means, these not being shown inasmuch as they are well known in the art. At the lower region of the machine is the gear box I4 containing an arrangement of gears operatively connected to the main drive mechanism, such as by means of gears connected to the shaft upon which said pulley I2 is mounted, such gearing arrangement also being omitted from the drawings because of their conventional construction. The drive shaft I5 operatively connected to the mechanism within gear box I4 and extending along the base of Iche machine is operatively connected to the feed dog bar I6 through the eccentric |1 and other conventional mechanism, said shaft I5 also being connected through the gear box I8 to the bobbin container |9, also in conventional manner, and hence need not be described herein in any greater detail.

Mounted upon the drive shaft I5 is an eccentric strap connected to the reciprocating arm 2| which, by means of the pin connection 22 extending through the elongated slot 23 of the rocker arm 24 (see Figures 4 and 5) is adapted to impart an intermittent rotary movement to the clutch mechanism 25 and upper roller shaft 26 in a manner to be hereinafter described.

It will be noted (Figure 4) that the said rocker arm 24 is shown integral with the rotatable hub 21 which extends into the drum member 28. By referring particularly to Figure 5 it will be seen that said hub member 21 contains four projections 29 in cross formation, providing four chambers 30 within which are operatively accommodated the rollers 3|. The lbase portions 32 of each chamber connecting adjacent projections 29 are somewhat tapered or eccentric with respect to the shaft 26, thereby rendering each of said chambers smaller at one end than at the other. Each of said chambers is also provided with a spring element 33 in engagement with the said rollers. The bushing 34 also projects into said drum-like member 28, as will be clearly seen from Figure 4, and also contains projections similar to those identified by the reference numeral 29, forming chambers therebetween similar to chambers 30 of Figure 5, the floors or bases of said chambers sloping in a direction opposite to that of bases 32 above referred to. Contained also within the chambers of bushing 34 are the roller bearings 35, as shown in Figure 4. The assembly of bushing 34, drum 28 and member 21 form a conventional roller-wedge-clutch adapted for intermittent operation upon an operative rocking movement of arm 24 in a manner to be hereinafter set forth.

It will be noted that the drum member 28 contains a middle wall 36 into which extends the screw 31 in abutting engagement with the shaft 26, thereby rendering member 28 immovably attached to shaft 26. The set screw 38 extending into the stationary frame 39 is in abutting engagement with the bushing 34, so as to hold it against movement.

The operation of the said clutch 25 can best be understood -by considering the movement imparted to rocker arm 24 by thev arm 2| due to the eccentric drive. It is obvious that upon a clockwise movement of said arm 24 (see Figure 5), the rollers 3| will become wedged between the upper and lower walls of the chambers 30 at the reduced portions thereof. But inasmuch as the upper wall of the chamber is part of the drum 28, and the lower wall part of the member 21 actuated by rocker arm 24, a continued clockwise movement of said rocker arm will cause a corresponding movement of the drum portion 28 which will carry with it, through the medium of screw 31, the shaft 26. Inasmuch as the rollers are also positioned within chambers the floors of which are disposed opposite to those identified by reference numerals 32, a continued movement of the drum 28 in the same direction as above referred to will merely cause it to be in rotatable engagement with the said rollers 35 which are now positioned in the enlarged portions of their corresponding chambers, formed by the overhanging flange of drum 28 and bushing 34, which, as aforesaid, is held aiiixed in place by means of the screw 38. Hence upon a clockwise movement of arm 24, the shaft 26 will also rotate in a clockwise direction Within bushing 34 as one of its bearings. In the event however, the said rocker arm 24 is rotated in a counterclockwise direction or moved upwardly (refer to Figure 5), the member 21 will be free to rotate about the shaft 26 while in engagement with the rollers 3| which will obviously be brought to the enlarged portion of their chambers. Under these conditions it is obvious that the drum member 28 will not be operatively actuated Iby the movement of member 21; and because of such freedom for relative movement, an upward movement of rocker arm 24 will have no effect upon shaft 26. It is thus apparent that shaft 26, with the arrangement illustrated, will be rotatably actuated only when the rocker arm 24 is moved downwardly in accordance with the position thereof illustrated in Figures 4 and 5.

Positioned at the forward or head portion of the machine and somewhat to the rear of the presser foot 40 are the two tension rollers 4| and 42, these being yieldably held in engagement and synchronously actuated in a manner to be hereinafter set forth. In the preferred form of this invention, the upper roller 4I is knurled, Whereas the lower roller 42 is preferably smooth. The said upper roller 4I is mounted upon a front shaft 43 which is connected to the said shaft 26 by the intermediate transmission shaft 44 provided at its terminals with the universal joints 45 and 46, the rear end of said shaft 44 being shown connected to a rear shaft 41 provided with longitudinal rods 48 in slidable operative engagement with correspondingly recessed portions in the adjacent terminal of said shaft 26, as clearly shown in Figure 4. The shaft 43 is rotatably supported by a bearing 49 constituting part of the arm 50 which is mounted upon and affixed to the roller lifting shaft 5|. This latter shaft is rotatably supported by the bushings 52 and 53 mounted within the tubular support 54 which extends through a suitable aperture in the frame 39 and is held in xed position with respect thereto by means of the set screw 55.

Surmounted upon said tubular support 54 is the collar 56 which has anchored thereto one terminal of the helical spring 51 mounted over tube 54 and having its forward terminal suitably anchored to the arm 50, as clearly shown in Figure 4. Suitably mounted upon said collar 56 and the boss 58 of arm 58 is the tubular housing 59 which serves not only as a housing for the spring 51 but also as a spacer between the collar 56 and the arm 50, The said collar 56 is rotatably mounted upon the tubular element 54 and adapted to be held aflixed thereto in predetermined position by the set screw 60 whereby the tension in spring 51 can be regulated by rotatably manipulating the collar 56.

Suitably keyed to the rear terminal of lifting shaft I is the lifting lever 6I' which, when moved downwardly or in a counterclockwise direction (see Figures 4 and 5) will obviously cause a rotation of shaft 5I a consequent lifting of arm and a separation of roller 4I from its coacting roller 42. Positioned preferably above the arm of lever 6I is the eccentric cam B2 engageable with arm 6I upon a rotary manipulation of arm 63. By manipulating said lever 63 upwardly (see Figure 4) it is apparentA that the cam portion 62 will serve to move or keep the lever 6I in its lowermost or depressed position. It is thus apparent that if it is desired for any reason whatsoever to maintain the roller 4| in a raised position so that it will not coact with its complementary roller 42 and hence not at such time serve as a tensioner, an operative manipulation of lever 63 can readily accomplish this result without in any way affecting any of the other operative parts of the machine, asf

will more clearly appear from the description hereinafter given.

The presser foot 4B is operatively connected with the manual presser foot lifter 64 as in most conventional sewing machines. In the structure illustrated, the said lifter 64 is operatively engageable with one terminal 65 of the presser foot lever 65 rotatably mounted at Il, the terminal 58 of said lever being suitably attached to the link 69 extending vertically downwardly' so that the lowermost terminal 'I0 thereof is in operative engagement with one terminal of the knee-pressure lever II rotatably mounted at T2. The forward' end 'I3 of said lever 'I.I is adapted to be actuated in the direction of the arrow A (see Figure 1) by any conventional means operated by foot or knee pressure, the details of such construction not being illustrated inasmuch as it is well known in the art. Suitably secured to the link 69 is the block 'I4 containing pin 'I5 upon which is rotatably mounted the bar 'IS the lowermost terminal thereof containing the elongated slot TI within which the pin I8 of the arm 6I is slidably movable.

Suitably mounted upon the rear portion of shaft 26 is the gear 'I9 which is in operative engagement with the gear 80 mounted upon the shaft 8| to the forward terminal of which the lower roller 42 is attached. The diameters of gears 19 and 8d, and of rollers 4I and 42, are so designed that the peripheral speeds of each of the feeding rollers will be exactly equal to each other, so that there will be no slippage between these rollers.

In the operation of this machine, particularly for the formation of hemmed edges, the rollers 4I and 2 are, as aforesaid, in operative engagement under normal working conditions. The material is fed from the platform 82 to the conventional serrated feed dog 83 operatively connected to the aforesaid feed dog bar I6 illustrated in Figure 2. This coacts with the presser foot 4D and the needle 85 in conventional manner to cause stitches to be formed and the material to be fed rearwardly. In the construction illustrated and forming part of my invention, the material moves rearwardly under the guide 85 the terminal of which is positioned near the line of engagement of rollers 4I and 42. As will more clearly appear from the description hereinafter given, the material is engaged by these rollers and pulled rearwardly against the grip of the feed dog, thereby producing the desired tension during each feeding movement that will be effective in eliminating warping. It will be observed that both sides of the material are being securely engaged by cooperating feed mechanisms, the upper surface by the rearwardlyv disposed knurled upper roller 42 and the undersurface by the forwardly disposed serrated feed dog 83, the said knurled and serrated surfaces reducing the possibility of unwanted slippage.

In accordance with conventional construction and operation, the rotation of the drive shaft I5 from gear box I4 produces certain rearwardly directed feed movements of the said feed dog 83, there being generally one such movement for each revolution of the shaft I5. By properly designing and positioning the eccentric 2D and associated mechanism, operative rotational movements of both the rollers 4I and 42 can be obtained in predetermined synchronous relation with respect to the aforesaid feed movements of the feed dog 83, the eccentric movements imparted to the reciprocating arm 2I causing -corresponding operative movements of the rocker arm 24 and the uni-directional clutch mechanism 25 above described, and consequently producing corresponding movements of the parallel roller ctuating shafts 25 and BI. By this means it is apparent that the tension rollers 4l and 42 yare operatively actuated only when the feed dog 83 is actuated, so that both mechanisms may operate in coactive relation. And by this means the material as well -as the sewing thread are both kept under constant tension during the sewing operation, inasmuch as the rollers are exerting a pull away from the feed dog mechanism.

The resilient, tensile and other properties of different materials may render it necessary to alter the timing of the rollers li and l2 with respect to the operative feed movements of the feed dog mechanism. Individual cases may hence require that the tensioning rollers operatively engage the material either before, during, or after the regular rearward feeding movements imparted to the material by the feed dog. To enable the mechanism to be adjusted to meet such varying conditions, the eccentric 20 is made rotatably adjustable, as clearly indicated in Figures 5 and 6.

As illustrated, the eccentric mechanism contains a sheave 23a which has preferably integral therewith the hub 9) rotatably mounted over shaft i5. Extending through said hub is the set screw 9| which is in abuttable engagement with said shaft I5, in conventional manner. By rotating eccentric sheave 20a to any desired position, and holding it locked in that position through the medium of said screw 9i, the rotation of the rollers 4I and 42 can be timed in `accordance with any predetermined setting. This is obviously due to the fact that the arm 2l is reciprocatingly actuated by the eccentric sheave 26a, the lower portion of the arm being in rootatable engagement therewith. The throw of the eccentric mechanism can thus be made to occur at any predetermined time with respect to the rotation of shaft I5. Inasmuch as the feed dog mechanism is also operated through the medium of shaft I5, the arrangement is such as to enable the tensioning rollers III and 42 to be operatively actuated in predetermined timed relation to the feeding movement of the said feed dog mechanism.

In a preferred setting of this machine for most commonly employed materials, the eccentric mechanism is so adjusted as to cause the tensioning rollers 4I and 42 to begin operating after the completion of each feeding movement of the feed dog. In this manner the material will be periodically held by the feed dog mechanismv and then pulled away therefrom and stretched by the rollers after'each feeding movement, to lproduce the desired effect. It is of course obvious that the operation of the tensioning rollers can take place at any other time with respect to the feeding movement of the feed dog mechanism, and may occur either before, during or after the completion of the rearward feeding movements imparted to the material by the feed dog. The device is hence readily adaptable for different conditions of operation, and for materials of various properties.

In the design of this device, it is preferred that the peripheral rotational speed of the tensioning rollers 4| and 42 be somewhat greater than the linear feeding movement of the feed dog mechanism. With such an arrangement, there will always be a rearward tensioning pull eifectuated by the rollers even when they are operatively actuated during the feeding movement of the feed dog. In this manner the material is prevented from puckering or gathering at all times, regardless of the relative timing between the tension rollers and the feed dog mech anism.

Not only is the timing of the rollers an important factor in rendering this device adaptable for materials and threads of different properties, but the extent of the peripheral rota-ry movement of the rollers is likewise a controlling factor. The extent of such movement for each intermittent actuation of the rollers can be varied by moving the pin 22 into a predetermined position within the slot 23 (see Figures 4, 5 and 6) and immovably affixing said pin in such selected position by means of the nut and ,bolt arrangement 86, whereby the stroke of the rocker arm 24 and consequently the peripheral movement of the shaft 26 and rollers 4| and 42, can be controlled. For example, should it be desired to increase the operative movement of the said `rollers 4| and 42 for each operative revolution of the drive shaft l5, the said pin 22 is moved towards the left of the slot 22 (Figure 5) whereby a greater movement of rocker arm 24 will be obtained, and consequently a greater peripheral movement of the said feed rollers.

A modified form of my invention is illustrated in Figures 7 and 8 in which provision is made for a compensating adjustment of the eccentric sheave in a direction transverse with respect to the axis of the main drive shaft I upon a rotational positioning of the sheave on said shaft in accordance with a predetermined setting. More specifically, the reciprocating arm 21a, is provided with the eccentric 20c mounted over the eccentric sheave 93. Mounted over shaft I5 adjacent the said sheave 93 is the coupling 94 which is held in xed relation to the shaft by the set screw 95. In th-e preferred form of this arrangement, the eccentric sheave 93 is provided with a flange 96 in abutment with a flange 91 integral with the coupling 94. The flange 91B contains slots 98 therein disposed substantially transversely with respect to the longitudinal axis of shaft I5. Screws 99 extend through seid slots and are in threaded engagement with flange 91. The sheave 93 contains a central elongated aperture |00 also extending transversely with respect to shaft I5.

In setting the above described arrangement of Figures 7 and 8, the screw 95 is manipulated to release coupling 94, which is then rotated to any desired position on shaft l5. The screws 99 are also manipulated to release the flanges 96 and 91 from each other, and thereby permitting sheave 93 to be moved transversely with respect to shaft I5 because of the said elongated aperture |00. Thereafter the screws 95 and 99 are tightened to hold the eccentric arrangement in its new position. In this manner a double adjustment is made to obtain the proper and desired positioning of the eccentric 20c with respect to the pivotal connection at 22.

It frequently occurs, especially where elastic materials are to be sewed, that the operative rotational movement of rollers 4| and 42 continuesv beyond predetermined points due to the momentum of the rollers and the rotatable transmission members, particularly thel clutch 25, the shaft 26 and associated mechanism. To overcome this shortcoming, I have provided a braking mechanism actuated by the rocker arm 24. By referring to Figures 9 and 10, it will be seen that lthe rocker arm is provided with a brake-actuating pin |0| which is engageable with the contact bar |02 secured to the brake |03. The said brake is pivotally mounted on the framework |04 at |05. Upon a downward operative movement of rocker arm 24, which movement causes the tensioning rollers 4| and 42 to rotate in the manner above described, the pin |0I will engage the contact bar |02 to cause the brake |03 to frictionally engage the cylindrical surface of clutch 25. It is preferred that this action occur at the end of the downward operative movement of the rocker arm 24, thereby preventing a continued rotation of the rollers beyond such point. It is also preferred that-the contact bar |02 be adjustably positioned on the brake |03, such as ,by the slotted portion |06 and the set screw |01 extending into the body of the brake arm. In this manner the precise time of the braking action can be regulated in accordance with the particular conditions.

Should it be desired to raise the presser foot 40, such as for tacking operations, this could be accomplished by operating the knee pressure lever 1| by any conventional mechanism provided for that purpose. The construction is so arranged that when such pressure is applied, a. force in the direction of arrow A (see Figure 1) will be applied to the terminal 13 of the lever 1I, to cause a downward -movement of link 69, and a corresponding movement of the block 14 and bar 16. This will cause the upper terminal wall of slot 11 to engage the pin 16 and move the arm 6|` downwardly (see Figures 1, 3 and 4) in a countercl'ockwise direction, to cause a corresponding rotation of lifting shaft 5| and an elevation of arm 50 to cause a consequent separation of roller4| from roller 42, all against the action of spring 51. This obviously is rendered possible by virtue of the universal connection of shafts 43 and 26 above described.

When the rollers are thus separated it is obvious that they cannot perform any tensioning operation, thereby permitting a tacking operation to be effected by the operators moving the material forwardly and rearwardly in conventi'onal manner, this being further rendered possible by the fact that the aforesaid downward movement of link 69 has caused an upward movement of the forward arm of lever 66 and a consequent raising of the presser foot 40. This arrangement is of particular importance in production work where flat unwarped hems must be produced upon a succession 'of pieces fed through the machine, the tacking operation lbeing performed at the end of one piece and carried over to the beginning of the new piece, the connecting threads to be severed at a subsequent time.

This device is further adapted to permit the rollers 4l and 42 and the conventional feed mechanism including the presser foot 4U and feed dog 83 to simultaneously accommodate a piece of material of varying thickness. When the material is being fed by the feed dog 83 and has not as yet reached the rollers, the feeding is accomplished in conventional manner, and the rollers are in actual Contact. As soon as some of the material enters the roller mechanism, the said rollers must of necessity be separated due to the thickness of the material therebetween. This is rendered possible by the arrangement of the slot 'H which extends below the position of pin 'I8 in its normal position (Figure 3). When the rollers are separated by the interposition of material as aforesaid, the arm 50 will be rotated in a counterclockwise direction about shaft 5|, permitting a lowering of the pin 18 within the slot '11. Also, should the material be of varying thickness, the rollers will be permitted to adjustably separate a corresponding amount as the material is being fed through, by virtue of the said slot TI.

Should it be desired to operate this machine in conventional manner without the use of the roller mechanism, all that need be done is to detach the bar 16 from the block 14 by removing the cotter pin 8l, and then operatively raising roller 4l through the medium of arm 6| in the manner above described, maintaining said lever 6l in this position by operatively manipulating arm 63 with its eccentric portion 62, all as aforesaid. The rollers being separated, and the pressure foot mechanism being disconnected from the roller feed mechanism, the machine is obviously adapted for conventional operation.

Note should also be taken of the fact that the material being sewn can readily be removed from the machine by simply raising the manual lifting bar B4 or operating the knee presser apparatus in a manner above described, which will cause an elevation of the presser foot 4|] and the roller 4l, thereby enabling the material to be readily disengaged from the machine.

Although the construction hereinabove described illustrates the eccentric 2l! as being operatively associated with the shaft I5, it is obvious that it can be in operative engagement with other portions or at other points of the main drive, the particular disposition of the said eccentric being merely illustrative of one possible design within the contemplation of my invention. The eecentric motion may obviously be just as readily obtained from the upper shaft along the axis of the pulley I2, also forming a part of the main drive, within the contemplation of this invention.

It is of course understood that the various embodiments above described and shown in the drawings are illustrative of my invention and not employed by way of limitation, inasmuch as numerous changes and modifications may be made within the scope of the appended claims without departing from the spirit of this invention.

What I claim is:

l. In a sewing machine, a table upon which the material to be stitched is positioned and operatively movable during the sewing operation, a feed dog mechanism having a presser foot associated therewith, a pair of coacting rollers in spaced relation to said mechanism and adapted to operatively engage therebetween the material fed by said mechanism, a main drive shaft, rotary transmitting means operatively associated with said rollers, rocker means operatively connected to said transmitting means, eccentric actuating means connecting said drive shaft and said rocker means for imparting intermittent rotary movements to the rollers, transmission means operatively connecting said shaft and the feed dog mechanism,v brake means operatively engageable with said rotary transmitting means, and brake-actuating means on said rocker means for operating said brake means.

2. In a sewing machine, a table upon which the material to be stitched is positioned and operatively movable during the sewing operation, a feed dog mechanism having a presser foot associated therewith, a pair of coacting rollers in spaced relation to said mechanism and adapted to operatively engage therebetween the material fed by said mechanism, a main drive shaft, rotary transmitting means operatively associated with said rollers, a rocker arm operatively connected to said transmitting means, eccentric actuating means connecting said drive shaft and said rocker arm for imparting intermittent rotary movements to the rollers, transmission means operatively connecting said shaft and the feed dog mechanism, brake means operatively engageable with said rotary transmitting means, a brake-actuating pin on said rocker arm, and a Contact bar adjustably secured to said brake means and engageable with said pin during an operative movement of said rocker arm.

CHARLES MEYER.

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