USRE19812E - Balancing machine - Google Patents

Description

Jan. 7, 1936. A F MQYER ET AL Re. 19,812

BALANC I NG MACH INE original Filed May 2. 1924 4 Sheets-sheet 1 Jan. 7, 1936.

A. F. MOYER ET AL BALANC ING MACHI NE original Filed May 2, 194

4 Sheets-Sheet 2 Jan. 7, 1936. A |=l MOYER Er AL Re. 19,812

BALANCING MACHINE Original Filed May 2, 1924 4 Sheets-Sheet 3 um@ B;

Jan. 7, 1936. A. F. MoYER l-:r AL Re. 19,812

BALANCuING MACHINE Original Filed May 2, 1924 4 Sheets-Sheet 4 Reissued Jan. 7, 1936 Re,

19,812 BALANCING MACHINE Amos F. Moyer, Minneapolis, Minn., and Francis T. McDonough, deceased, late of Madison, Wis., by Precision Balancing Machine Company, Eau Claire, Wi., assignee, by mesne assignments Original No. 1,812,353, dated June 30, 1931, Serial No. 710,595, May 2, 1924. Renewed October 21, 1927. Application for reissue February 5, 1932, Serial No. 590,999S

' 2s claims. (c1. 73-51) The balancing machine of our invention and of a base on which is pivotally mounted a recshown herewith is oi' a type adapted to make tangular frame or supporting means capable of determination of unbalance to be corrected by oscillation under spring restraint. At one end oi application or removal of weight at determinate said frame is a headstock carrying a ball bearing angular positions in each of two arbitrarily se- 'ily wheel and correction disk, while intervening lected planes of the work, establishing thereby between said headstock, and the pivotal support complete dynamic balance, including static balis a cross member with the two adjustable ball ance. Disclosures are herein made which would bearing rollers to support the adjacent end o1'. be equally applicable to balancing machines in the work. Beyond said pivots is a similar cross which static balance is established prior to demember with adjustable rollers to support the 10 terminlng dynamic unbalance. Likewise, the overhanging end of the work. All of these memmachine of our invention is of the type in which bers, namely, the headstock and two cross supthe revolving body is caused to rotate first at a porting members, are longitudinally adjustable to speed higher than the critical speed oi the repermit bringing an arbitrarily selected transverse i5 silient supporting means, and then permitted to plane of the work into coincidence with the pivots. 15 revolve freely upon ball bearing supports while a procedure essential to direct measurement of the rotative speed gradually diminishes from the correction required in each oi two arbitrarily above to below the critical speed, thereby setting selected planes of the work. A second transverse up a maximum amplitude of oscillation of the plane of the work may be brought into coincisupporting means as critical speed is passed dence with the pivots either bylongitudinal move- 20 through, which maximum amplitude is a directly ment of the members on the frame or by interproportionate measure of the unbalance to be changing the two ends of the work. In detail determined. Features are also disclosed which arrangement this machine represents only one would be equally applicable to a machine of conof many possible constructions, and the specinc stant speed power driven type. reference to the relative location of parts is here 25 Among the novel features of this invention are: given for reference purposes only, or to signify A resilient pivotal mounting of the supporting apreferred construction. means'which is adiustable as to the supporting In the several views of the drawings like charstrength o1' the resilient members in accordance acters have been used to designate identical with the weight o1' the work and the natural parts. 30 period or critical speed oi' oscillation, besides Figure 1 is a front elevation oi the complete vbeing frictionless in its oscillation save for the machine empty oi' work. internal hysteresis oi' springs and for atmos- Figure 2 is a plan view of the complete machine pheric resistance. A ily wheel and universally showing a crankshaft in place as work to bel adjustable balance weight are carried by the supbalanced.

porting means, to which the work may be ad- Figure 3 is an elevation taken from the lei't justably aligned, and which by its rotative inof Figure 1. ertia controls the rate at which the revolving Figure 4 is a section taken on the line AA of work passes through the critical speed. Friction- Figure 2.

40 less flexible means for connecting without con- Fgure5 is a section and partial elevation taken 40 straint the work, with a source of driving power on the line BB oi' Figure 4. or flywheel control, including revolving parts Figure 6 is an elevation and partial section through which quantities o1. counter-balance may taken 0n the line CC of Figure 4. be applied. 'I'hese revolving parts are installed Figure 7 is apartial section shown in perspec- UNITED STATES PATENT OFFICE on the machine for the application and positiontive taken on the line DD oi Figure 2. 45 ing of. counter-balance equivalent to the correc- Figure 8 is a rear quarter perspective taken tion determined for the work. Frictionless adfrom position EE oi' Figure 1.

Justable means for actuating an amplitude indi- Referring to Figure 1, I is the base on which is cator from the oscillations of the supporting the supporting member le. Clamped to the supmeans are provided. A retaining lock and reporting member, I, in transverse alignment, are 50 leasing device for locking the supporting means two plate spring pivots 2, to the upper edge oi' at the neutral position of rest and releasing same which are clamped supporting members I* which without jar or false disturbance when amplicarry the rectangular frame 3. The right extudes oi' oscillation are to be observed. tremity oi' frame 3 is adjustably connected by a In general arrangement the machine consists screw t to a gooseneck spring 5 carried on the 55 iree end of a cantilever spring 6. The left end of the spring I is attached to the left supporting member Ih and at an intermediate lpoint the spring 3 is secured by clamp blocks 1 and 1 to a slide l, the free length of the spring 3 which lies adjustable by a slide l. arrangement the natural vibratory period, or critical speed, of frame 3 may be varied at will, since the sh'orter the free length of the spring 3, the more rapid will be the vibratory period of the frame 3, and the longer the free length of the spring 3 the more slow will be the vibratory period or critical speed. The adjustabillty of critical speed is of particular advantage whenlchanging the set-up of the machine to a piece f work of different weight. for an increase in weight of the work overhanging the pivots will cause a slower critical speed, so that without this adjustment a different spring would be required for every setup, in order to arrive at the same critical speed. Also the required adjustment to increase a critical speed thus reduced by an addition of weight will be a shortening of the cantilever length of spring B. which at the same timewill increase the strength of the spring tc support the additional weight. The machine is, therefore, adapted to a wide variety in the weight of work. Since the total support of frame 3 is effected through springs 2, 5 and 6, which have all joints securely clamped and 'no mechanically journalled connection, there is no frictional resistance to oscillationl other than atmospheric resistance, and internal hysteresis of the springs. The latter hysteresis of springs is smaller than the friction of any known mechanical pivot or journal, and the sensitiveness of the machine to small amounts of unbalance is accordingly very great, in view also o'f the light weight construction of the oscillating frame which is designed for necessary mechanical strength only, and not for rigid alignment of par. The elimination of friction in the oscillation of the frame is essential inA order that amplitudes of oscillation may be directly proportionate measures of amounts of unbalance.

longitudinally adjustable at the left end of the frame 3 is a headstock frame 3 which carries a ywheel III supported in ball bearing journals I I, shown in Figure 4. Rtatably mounted on the hub of flywheel I0 is a correction disk I2 which is locked against relative movement upon III by means of the threaded clamping wheel I3. The web of disk I2 is slotted radially to receive the -adjustable weight I4, vernier, block I5 and clamping knob I3.. the combined weight of which is carefully standardized so that movement of this assembly a known radial distance will correspond to a known quantity of unbalance. For example, a weight of ten ounces moved one inch represents a change in balance. or a quantity of unbalance equal to ten ounce-inches.

InFigureareseenaclamping knob Nanda vernier block Il, which is movable radially adjacent to graduated scale I2.. Block I6 carries graduations forming ten equal divisions having a total combined length equal to nine divisions on scale I2, thus aifording vernier readings of position within one-tenth of the smallest divisions on With the weight set at the inner positionorseroreading, disk I2isinperfectindependent balance and can be turned to any angular position with respect to flywheel Il without up- Flywheel Il,togetherwith all other members mounted to revolve on jour- `will permit, and is nals I I is also in perfect balance. Radial adjustment of weight assembly, I4, I5, I8 combined with angular adjustment of disk I2 permits the application of balance corrections of any desired magnitude or angular pomtion. Shouldthemagnitude 5 oi' the desired correction be greater than permitted by the outer extremity of the adjusting slot, two threaded openings I2b are provided, in which may be inserted equal known weights permitting assembly I4, I3, I3 to be set back to zero, and thence proceeding by addition as with the rider on a scale beam after adding weights to the pan.

The periphery of ywheel III is graduated with angular divisions referring to an index point on the rim of the disk I2, so that any desired angular position for disk I2 may be readily set off.

For purposes of setting the revolving work into motion, as for example by hand or power friction applied to flywheel Ill, and in order that 29 the inertia of said flywheel may be transmitted to the work, said flywheel is rigidly mounted on tubular shaft I1 journaled in ball bearings Il and connection is made to the work as follows. At the left end of the shaft I1 is a tapered soft collet 25 I8 which by means of nut I3 engages the internal shaft 20, passing through the tubular shaft I1.

The right hand end ofthe shaft 20 is engaged by means of threaded collet 2l and hub 22 to 'a cup 23, the split sides of which engage the work 30 by means of clamp collar 24, which is locked by screw 25. Shaft 20 is purposely made slender and of considerable length in order to be as flexible as possible, being preferably of spring material so as to permit slight flexure between the 3;, work and the headstcck without restraint upon the bearings. In order to prevent torsional vibration between the work and the flywheel, which otherwise would occur through the elasticity of the shaft 20, a tangential driver 23 is engaged 4;, to clamp the collar 24 by means of a grooved washer 26 and a nut 21, and at the other end is engaged by means of beveled washers 30 and a nut 3l to pin 32 set in the face plate 33, which is in turn rigidly mounted on the shaft 4;, I1. The parts upon the pin 32 are counterbalanced by the pin 34, and a collar 24 is perfectly balanced with the driver 23 engaged. Driver 2l is also as slender and exible as requirements preferably of spring material. 50

The work is carried upon four ball bearing rollers 35, each cf which has independent vertical adjustment by means of a screw 36 and a nut 31, being guided by a key 33 and locked by clamp screws 33 to the supports 40, which are separately 55 adjustable on cross members 4 I 'I'he four screws 36 are adjusted to place the rotative axis of the work in alignment with the rotative axis of the shaft I1 when the frame 3 is at rest. Internal shaft 20 and a. driver 2l are then engaged wlthco out strain so that the only forces acting upon the frame 3 are the forces of unbalance in the revolving bodies.

In order that the maximum amplitude oir oscillations taken as critical speed is passed through c5 may be a directly proportionate measure of the amount of unbalance, it is necessary that the frame 3 be locked against oscillation during the time that the revolving parts are set In motion at a speed above critical speed, and that the frame 3 be thereupon released from a truly neutral position of rest and permitted to act without interference or false jar under the disturbing forces of unbalance only. A gradually redingtouchofthehandorilngerwiilservethe purpose but mechanism means for effecting the result are shown in Figure 7. Upon the left cross member of the frame l is a forked member I2 adjustably locked in position by a clamp bolt or bolts 49. Upon the transverse faces of th depending forked portions of 42 are mounted `lfour spring members M so attached to I! at their upper ends that the lower ends diverge from a position of contact with said faces unless forced into contact by the application of a transverse pressure. Parallel with said member of the frame 3 and passing between the forked portions of 42 is a shaft I5 upon which are screw threads I8 and Il respectively of right hand and left hand pitch. Engaging these threads respectively are threaded clamp Jaws Il and 49, which are slidably guided on a pin 50. A clockwise turning of shaft I5 will therefore cause the blocks Il and 49 to move toward each other, while a counter clockwise turning of shaft 45 will cause a reversed movement.

In order that frame I may oscillate without friction jaws 48 and 49 must separate sumciently to remain completely out of contact with springs u, collar 5I being employed to limit excessive movement in this direction, and to guide the operator in obtaining the correct position of freedom. When there is no disturbing force acting upon the frame 3, any residual of vibratory oscillation may be readily damped out with this device by bringing jaws 49 and I9 into contact with springs 44 'and gradually receding to a position of no contact. The gradually diminishing friction between the contacting surfaces will thus bring frame 9 to rest at the neutral position. In order that this process may be most eil'ective, it is desirable that the contacting faces of springs M and jaws 49 and 49 be well smoothed and highly polished. Frame 3 is locked by bringing jaws 49 and 49 forcibly together to clamp members 44 and l2 as in a vise. Shaft l5 is actuated by a lever 59 seen in Figures 1, 2 and 3.

proportionality of observed amplitudes of oscillation is of prime importance in the process employed on this machine. and since the obtaining of proportionality between such amplitudes and quantities of imbalance necessitates the absence or a very great reduction of frictional resistance to oscillation, an amplitude indicator is required which consumes the smallest possible energy in friction, and at the same time gives visual indications or readings of suitable proportionate size for numerical interpretation of the smallest quantities to be dealt with in practice. Likewise the largest amplitudes to be encountered must be within the range of observable readings on the indicator, and an adjustment of the indicator permitting a variation of the scale of the readings will be useful in that the movement of the indicator hand when observing large amplitudes of oscillation need not be so great in linear velocity as to render observations both diilicult and inaccurate.

Figure 8 shows the mounting of an indicator of the type employed by machinists for observing the accuracy of metal parts: such an indicator, if possessing small frictional resistance, being adapted to the purpose because of the small necessary motion of the actuating parts and consequent small energy of friction. By the mounting here shown, the indicator is placed in a position convenient to careful observation by the operator, and is provided with an adjustment permitting variation of the scale of readings. 54 is a column supported on pedestal i of the base and carrying head 55. Clamped horizontally to 55 is a leaf spring 58 which when free is so upwardly curved that upon being drawn down by the wire 51 and attached to ythe frame I at its neutral position of rest, it has a position 5 and contour when so restrained, which is substantially horizontal and straight. Vertical oscillation of the frame 9 will then be accompanied by a proportionate vertical movement of all portions of the free length of the spring 59. the mag- 10 nitude of such movement being greatly diminished as the point considered approaches nearer the point of rigid attachment between the spring 56 and the head 55. Also carried by the head 55 on the column Il is an arm 59 mounting a 15 rod 59, upon which is slidably mounted a sup-- port 50 which may be locked in position by means of a thumb screw 8l. The indicator 92 is mounted upon a support 60 with its actuating ball point il resting upon the spring 59 so that 20 oscillation of the frame 3 and spring 58 are indicated by movement of the dial hand of indicator 52, which is at the obverse side as seen in Figure 8. By virtue of substantial parallelism between spring 5B and rod 59, the support S0 25 may so be moved along the rod 59 as to vary the proportionate oscillations of the ball 63 and hence to change the scale of movement shown by the dial hand of indicator 92. Adjustable stop collars M and 55 may be set at determined posi- 30 tions on rod 59 representing two locations of indicator 62 which may be found adapted to two varieties of work, or diil'erlng from each other by a predetermined ratio between the scales of movement observed at the indicator dial hand. 35

For example, when support 80 is adjusted to the limiting position in contact with collar 6I, the movement of the dial hand on indicator 62 for a given amplitude oi' oscillation of the frame 3 corresponding to a given amount of unbalance 40 may be exactly one-tenth oi' the corresponding movement of the dial hand when support 60 is in contact with the collar 55. The latter position of indicator 92 is accordingly adapted to observing small quantities of unbalance, and the former 45 to observing large quantities of unbalance, and the proportional relationship between quantities of unbalance and observed amplitudes may be readily retained numerically by proper positioning of the decimal point. 60

We claim as our invention:

l. In a balancing machine, a base, a support for the body to be balanced, resilientmeans on said base mounting said support for substantially pivotal vibration, said resilient mounting 55 means being located in a correction plane of the body to be balanced, a resilient cantilever on said base, and flexible means connecting said cantilever to said support permitting relative movement therebetween. 60

2. In a balancing machine with a pivotally mounted support for the revolving test body, a flywheel Journaled to revolve upon said support in substantial alignment with the test body, means adapted to revolve with said ywheel com- 65 prising a weight adjustable with respect to said flywheel both to known degrees of unbalance and to known angular positions, connecting means comprising a flexible member transmitting tangential forces to interconnect said flywheel and test body, and anti-friction bearings for said body and for said flywheel.

3. In a balancing machine, a base, a support connected to said base to oscillate and to revolvably carry, a test body. means to rotate the body, retaining means on said support, means mounted on said base for exerting pressure on said retaining means and for gradually releasing said pressure, and resilient frictional means interposed between said retaining means and pressure exerting means, whereby said support may be frictionally retained against oscillation, or said friction may be gradually reduced to permit said support to oscillate while said body is rotating.

4. In a balancing machine, an oscillatable support for a revolving test body, a graduated oscillation amplitude indicator. means including a frictionless element operatively connecting said indicator to said support, and means for adjusting a connection relative to said irictionless element operative to vary the ratio between the oscillatory movements of said support and the movements shown by said'indicator.

5. In a balancing machine, an oscillatable support for a test body, a graduated oscillation amplitude indicator, means including a movable arm operatively connecting said indicator to said support, and means for varying the operative point of connection between said arm and said indicater eiective to vary the ratio between the oscillatory movements of said support and the movements shown by said indicator.

6. In a balancing machine, the combination with an oscillatory support pivoted in one of the two transverse planes selected for balancing corrections of the revolving test body carried thereon with means for measuring amounts of unbalance by amplitudes of oscillation, of revolving means on said support separate from the test bodv adapted for applying a predetermined amount of unbalance at a predetermined position, thereby producing the same resultant effect on the oscillatory support as would the required balancing correction if applied in the other of thetwo transverse planes for balancing of the tcst body, whereby the system may revolve without oscillation of said support.

'1. A balancing machine for revolving bodies comprising an oscillatable frame having ways parallel to the rotational axis of the body, a pivot controlling the frame to oscillate about an axis perpendicular to the rotational axis of the body, supports adjustable on said ways at opposite sides of the pivotal axis and adapted to carry a revolving test body with a selected transverse correction plane of the test body containing the pivotal axis; a head-stock also adjustable on said ways and carrying revolving parts coaxially with the test body and connected thereto, which are adaped for applying a determined amount of imbalance and for locating said unbalance at a determined angle with respect to the revolving test body.

8. In a balancing machine the combination with an oscillatory frame adapted to rotatably support a test body, said frame being pivotally restrained to oscillate transversely to the axis of the rotatable test body, of means revolving coaxlally with the test body for applying and locating balancing corrections and disposed at the opposite side of the pivotal support from the selected plane of the test body for which a correction is being determined.

9. In a balancing machine, a base, a support for the body to be balanced, means on said base mounting said support for substantially pivotal vibration, a resilient cantilever on said base, flexible means vconnected to said cantilever. and ad- Justabie means connecting said flexible means and said support.

l0. In a balancing machine for revolving bodies, the combination with a bed, a support for the body to be balanced mounted to oscillate on the bed 5 and provided with means by which said body may be carried while being free to revolve, means on said support arranged to be connected to the body to be operated, said means being adapted to have power applied thereto for revolving said body,10 means to lock said support against oscillation while said body is being revolved and to release said support after the body to be tested has been set in motion, thereafter permitting the body to revolve and the support to oscillate without me- 1;, chanical interference.

11. A balancing machine having a support for a revolving test body, the said support being mounted to oscillate about a pivot. a spring means connected to the support in a manner to influence 2o oscillations thereof, means for indicating the oscillatory positions of said support. and adjustable means connected to the spring means to cause said support to assume a desired neutral position when under static load, as registered by 2.', said indicating means.

12. In a balancing machine awork support adapted to oscillate, a cantilever spring having its free end connected to the work support in such manner that the natural vibratory period thereof may be varied by varying the effective length oi' the cantilever portion of the spring, the entire support and connection of the work support with the cantilever spring being eilected by means whereby there is substantially no frictional resistance to oscillation, means arranged upon the work support for rotating work and means adjustably connecting the work support and spring.

13. A balancing machine for revolving bodies having the combination of a support for the body, 40 mountings for said support permitting vibration substantially pivotal, a spring connected to the support and controlling the natural period of free vibration, locking means movable relatively to the support and permitting said support to be released 4:, or locked against vibration, and resilient friction members engageable with the movement of said locking means, whereby the locking means may be released, accompanied by gradual reduction of friction. Y

14. In a balancing machine, a base having a pivot member mounted thereon, a support revolubly'carrying the body to be balanced and mounted for vibration about the axis of said pivot, flexible means connected to said support and spaced from said pivot, a resilient cantilever operatively connected to said flexible means for controlling vibration of said support, and means for adjusting the stiffness of said cantilever for regulating the natural frequency of vibration of said support.

15. In a balancing machine with a support for the revolving body, clamping means having surfaces parallel to the natural direction o! vibration of the support, a retaining member secured to the support, means to exert or release a pressure between said clamping surfaces and retaining member, and resilient means interposed therebetween, whereby the frictional damping to vibration may be gradually diminished as said clamping means are released.

16. In a balancing machine with an oscillatory support for the revolving body, clamping means having surfaces parallel to the natural direction of oscillation o! said support, resilient means secured to said support'and extending between said 75 clamping surfaces, and means to exert or release a pressure between said clamping surfaces and resilient means, whereby the frictional damping to vibration may be gradually diminished as said t clamping means are released.

17. In a balancing machine having a resiliently mounted frame adapted to support a rotating body in a plurality of bearings, a spring comprising a portion of said resilient mounting, means for adjusting said spring as to the characteristic ratio of force increment to deflection increment between a polntof fixed support and the point of attachment of said'spring to the said supporting means, operating means comprising a shaft mounted on said frame to revolve in substantial alignment with the rotating body, and exible means transmitting' tangential forces between said shaft and body to revolve synchronously.

18. In a machine for balancing revolving bodies upon a vibratable frame, a flexible shaft connected to the revolving body in substantial axial alignment therewith, a hollow shaft iournaled on said frame, said hollow shaft surrounding said flexible shaft and being connected thereto near the opposite end from said body, and means ad- Justable with respect to balance canied hollow shaft.

19. In a machine for balancing revolving bodies upon a frame which oscillates about a reference center contained in a transverse plane intersecting the revolving body near one end thereof, a flexible shaft connected to said end of the body in substantial axial alignment therewith, a hollow shaft journaled on said frame, said hollow shaft surrounding said flexible shaft and being on said connected thereto near the opposite end from said body, and means adjustable with respect to .balance carried on said hollow shaft.

20. In a balancing machine, the combination with a support mounted to oscillate about a pivot in one of two transverse planes selected for balancing corrections on the revolving test body carried thereon, of revolving means on said support and iiexibly connected to the test body for applying a determinate amount of unbalance at a determinate position, thereby to produce the same resultant effect on the oscillation of said support as would be produced by the required balancing correction if applied in the other of the two transverse planes selected for balancing the revolving test body.

2l. In a machine for balancing revolving bodies having a support mounted to oscillate about a pivotcontained in a transverse plane intersecting the body. a flexible shaft connected coaxially to the body, a hollow shaft journaled on said support and enclosing said flexible shaft and connected thereto near the opposite end from the body, and means mounted on said hollow shaft for applying and locating balancing corrections for offsetting the unbalance to be corrected in a transverse plane of the body disposed at the opposite side of said pivot.

22. In a .balancing machine, a base having a pivot xed thereon, a frame mounted to oscillate about said pivot, supports on said frame 5 upon opposite sides of said pivot for carrying a rotatable test body. and means to adjust said supports and test body with respect to said pivot in a direction parallel to the rotational axis of said test body, whereby an arbitrarily selected correction planemay be made to contain said pivot.

23. In a balancing machine, a frame for rotatably supporting a test body and mounted for vibration about a reference center contained in a plane transversely intersecting the test body and intended to receive a balancing correction,

a headstock with a revoluble shaft having means for applying balancing corrections and mounted on said frame co-axially with the test body. and exible means for applying tangential forces betven said shaft and test body whereby said body may be revolved by said shaft.

24. In a balancing machine, a frame for rotatably supporting a test body and mounted for vibration about a pivot, a headstock with a revoluble shaft having means for applying baiancing correction and mounted on said frame coaxially with the test body, and flexible means for applying tangential forces between said shaft and said test body whereby said body may be revolved by said shaft.

25. In a balancing machine, a frame adapted to oscillate about a pivot, supports on said frame upon opposite sides of said pivot for carrying a rotatable test body with a selected transverse correction plane of the body containing said pivot. and a headstock carried by said frame and comprising revoluble means for applying unbalance of any desired amount and angular position. said 4o headstock and one of said supports being adjustable on said frame with respect to said pivot in a direction parallel to the axis of rotation of the' test body.

26. In a balancing machine, an oscillatable support. a test body mounted for rotation on said support, means adapted intermittently to revolve freely or to have power applied thereto for rotating said test body. pressure means for applying friction to said support to prevent oscil- 5o lation while said power is being applied, and means for gradually decreasing the friction produced by said pressure means on said support to permit said support to oscillate.

AMOS F. MOYER.

PRECISION BALANCING MACHINE COM- PANY, Assignee of Francis T. McDonough, Deceased, Y

By WILLIAM C. TUI'TS. President.

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