US2653424A - Shoe heel surfacing machine - Google Patents

Description

Sept. 29, 1953 J. P. QUlRK ET AL 2,653,424

SHOE HEEL SURFACING MACHINE Filed Dec. 5, 1947 5 Sheets-Sheet l INVENTORS JUSTIN P. QUIRK LUDWIG s. P. HAFNER ATTORNEY.

Sept. 29, 1953 J. P. QUIRK ET AL 2,653,424

SHOE HEEL SURFACING MACHINE Filed Dec. 3, 1947 5 Sheets-Sheet 2 E Q FIG. 2 a 226 a JUSTIN P. QUIRK LUDWIG e. P. HAFNER BY aha/5g 3 AT TOR NEY Sept. 29, 1953 J. P. QUIRK ET AL SHOE HEEL SURFACING MACHINE 5 Sheets-Sheet 3 Filed Dec. 3, 1947 FIG. 3

INVENTORS JUSTIN P. QUIRK LUDWIG G. P. HAFNER ATTORNEY Sept. 29, 1953 J. P. QUIRK ET AL 2,653,424

SHOE HEEL SURFACING MACHINE Filed Dec. 3, 1947 s Sheets-Sheet 4 FI/IIIIIIIIIIII INVENTORS JUSTIN P. QUIRK LUDWIG G. P. HAFNER BY MW ATTORNEY Sept. 29, 1953 J. P. QUIRK ET AL SHOE HEEL SURFACING MACHINE 5 Sheets-Sheet 5 Filed Dec. 5, 1947 FIG.5

5 R O T N E V m JUSTIN P. QUIRK LUDWIG G.P,HAFNE'R ATTORNEY Patented Sept. 29, 1 953 UN ITEZD 'AT Ni i i-CE.

. SHOE HEEL SURFAGING. MACHINE Justin P. Quirk and Ludwig G. 'P. Hafner,1'St.

Louis, M0.,.assignors, by mesneiassignments; to Quirk -Machinery Company, 1st, Louis, :-Mo., a

corporation of Delaware Application December 3, 1947;;SerialNo;789; 154

:8 Claims. ;1

' This invention pertains to a shoe heel surfacing machine, generally, and concerns itselfmore particularly witha device that is capable of performingsuch operations'as sanding a wooden heel, and bufiing polishingor otherwise operatingupon -a shaped or partially-shaped shoe heel, entirely automatically with the exception of: a loading operation.

Generally,' it. isan object of the invention to :provide a: machine of= the type described which when once; put in operation 1 will thereafter continuously and automatically perform surface operations uponshoe heels without manual intervention, manual loading excepted.

Morespeciiically, it i an object of the inventionto providea machine of the type described which-twill impartto a shoe heel the necessary complex motionsfor moving .the same against asurfacing tool-:whereby the latter -w-ill Y pass over and follow given contours. of the heel, the

instant invention .comprisesia' frame upon: which is mountedra shoe heel. surfacing tool-and shoe heel' feeding mechanism-whichlatter device, :in .broad terms of operation, feedsoromoves 'the shoe heel, against, the surfacing :tool. The heel surfacing tool,"per se, may take-anyoneor-sevr oral-forms, for example,-a wooden heel-sander, which includes a -continuou sabrasive strip .passed .around two 1 horizontally .r'disposed disc spools: one of; which .is powered to movethe strip longitudinally. The shoe heel Jfeeding .unit

powered by a separate.motor'-monnted1=on.:a bracket: whichis pivotally connected: .to: the frame in aimanner suchzthatithe, same. maysbe'z-moved toward: and away. from the 1 surfacing: tool. This sbracket supports a cradle which .:isa-mounted anaautomatic heel jack andzran. automatic 1111681 ejecting mechanism :.and "further [carries vthe :necessary -mechanisms, including. an ;.-automatic one-revolution: clutch, bywmeans .of whichrthe heel; jack rotated and ismovedrelativelto; the

surfacing tool with the complex movements, well known invthe art. :Additionally, a power-takeoff is associated with a central shaft of the shoe heel feeding unit which take-off powers. and controlsthemovement of two fingers adapted "to.givehadditionalmovements to the surfacing tool in timedsequence with. the movements of the heel feeding unit.

Other objects and advantages of the machine will become apparent as the specification 1 :pro-

ceeds' and Ya more comprehensive understanding of the invention will be afforded from the followingidetailed descriptionwhen considered in conjunction with: the accompanying drawings, in which Fig. 1 is a front-elevational view of a shoe .heel surfacing machine embodying the instant invention,

T-Flg. 2 is a top viewof the same,

Fig.3 is afront elevational view of the machines heelfeeding unit showing parts thereof :andillustrating itsmounting arrangement on the frame,

Fig-Ai isla side view of the machine, in par- :tial section:and .with parts removed for. clarity, showing details of its heel feeding unit, surfacing tool, andithe powerconnection through which lCOIlLtI'OlQOfQthB latter is effected in timed rela- ;tionship withathe operation of the former,

Fig; 5. is asfragmen-tary plan view .of the .machine,.with parts removed, illustrating the relativepositionsuof its surfacing tool control mechanism'andheel feeding unit,

Figufiisa-detailview, in side elevation, of an adjustable mountin bracket for attaching the heekfeeding. unit, to; the machine's frame,

Figs. 7.- and 8 are, side and bottom views, respectively of'a-.c1utch plate employed inthe rmachincis automatic one-revolution clutch,

tions on a shoe heel. It is especially well adapted to function as a sanding machine, however, and, by way of illustrative example, only, it Will be so shown and described.

With reference to Fig. 1, the machine comprises, broadly, a frame 2| which supports a shoe heel surfacing tool, or sander, 22 and a shoe heel feeding unit 23.

The sander 22, against which a shoe heel is turned by the feeding unit 23, includes two horizontally disposed disc spools 24 and 25 around which is passed a continuous abrasive strip, or sand paper belt 25. The spools 24 and 25 are rounded and are mounted for rotation on their respective shafts 21 and 28. For driving the shaft 223, an electric motor 28 is provided, which latter element moves the belt 26 in the direction of the arrows. An adjustably positioned brush 3| (Fig. 2) is supported on top of the frame 2| in a manner such that its bristles 32 ride against an inner surface of the belt 26 (Fig. 4) and hold the same firm at a point where the feeding unit 3 presents the shoe heel to the belt for performing the sanding operation.

Although the function of the feeding unit 23 has been described broadly, as that of presenting a shoe heel to its surfacing tool, it also performs numerous sub-functions, each of which requires its own specific mechanism. These mechanisms combine to form the feeding unit as a whole, and accordingly, each will be described as a part of it.

For supporting the various components of the feeding unit, a frame is provided which comprises a vertical member 33 (Fig. 3) and two horizontal members 3 1 and 35. The vertical member 38 has two bearing collars 36 and 37 formed as a part thereof which pass over, slide along, and pivot about a shaft 38, the latter element being retained in a shaft bracket 39. A stub shaft ii, which forms a part of the bracket 39 is passed into a block bearing 32 and is held therein by a collar nut 23. The position which the block bearing 2 occupies with respect to the frame 2| is determined, by a two-way adjustable mounting bracket 455 (Fig. 6) by means of which it is connected to the said frame.

Here, a rod-like extension 45 of the block hearing 42 is passed into a bore 46 of a first rigid bracket member 5?. A thumb screw 22, threaded into the ends of the extension 55 moves the latter longitudinally of the bore ,5 to adjust the position of the shaft 4|, which adjustment is maintained by a bolt 89 passed through a slot 5| into the extension 35. A key 52, positioned in keyways in the extension "55 and the bore 46, prevents the rotation of the former in the latter. Similarly, an extension 53 of the member i? is arranged in a second bracket member 54 to provide a second adjustment for the position of the shaft 4| at right angles to the first, a thumb screw 55, a lock bolt 56, and a key 5i completing the assembly. Here, the member 54 is secured to the fram 2| by an angle bracket 58.

The horizontal member 35 is passed over a shouldered end of the shaft 38 and is held thereon to pivot about said shaft between two thrust bearings 55 held in place by a shaft lock nut 6|. The member 35 pivots about the shaft 38 with the rest of the frame but does not more vertically as do the members 33 and 34.

The foregoing describes the means provided for mounting the heel feeding unit 23, on the frame 2| for certain of its movements with respect to the surfacing tool 28 and for making adjustments to their relative positions. Thus, it is seen that the members 33, 34 and 35 and all that they support are free to pivot about the shaft 38; that the members 33 and 34 are adapted to move vertically with respect to the shaft 38 and that the position of all three of these members, collectively, may be adjusted with respect to the surfacing tool 26; horizontally, by the thumb screw it; vertically, by the thumb screw 55 and tiltingly, by rotating the shaft bracket 39 in the block bearing 42. All of these movements and adjustments together with others to be described are given ultimately to a shoe heel which is supported for movement in the heel feeding unit in a manner now to be described.

With reference to Fig. 3, a heel (52 is supported in an automatic jack 63 which, in turn, is mounted for tilting movement in a cradle 34. In addition to being tilted in the cradle es, the heel 62 is rotated about an axis 85, known as the heel axis, and further given a lifting motion parallel to said axis. Power for operating the heel feeding unit is supplied by an electric motor 66 and is transmitted through an automatic single-revolution clutch El to a central drive shaft 68. This shaft, which mounts a shape cam 89 and a tilt cam ii, is connected by means of a double universal joint 72 and a slip joint i3 (Fig. 4) with a revolving base of the jack 53, the universal slip joints providing for the positive rotation of the heel jack during the time it is being tilted in the cradle 64. Additionally, power is taken from the central drive shaft 68, by a sprocket wheel l5 and chain drive '55 for purposes yet to be described. Also forming a part of the heel feeding unit 23 is an automatic heel ejector ll (Fig. 3) and a heel loading guide 78. Beginhing with the cradle 62 upon which the automatic heel jack 5:53 is sup-ported for tilting action, each of these mechanisms of the heel feeding unit will be described in greater detail, although possibly not in the order given.

The cradles $4 comprises a horizontal base member 19 from which arises a vertical member 8|. Through this last mentioned member a bolt 82 is passed into the frame member 33 (Fig. 5), the bolt 82 serving as a pivot about which the cradle tilts. Depending from the base member 19 is an apron 83 (Fig. l) which supports a cam roller for contact with the tilt cam 1|. The cam roller 84 is bearinged in a movable arm 85 which is vertically adjustable in a slot 88 (Figs. 3 and 4) in the apron by means of a thumb screw 81 passed through the member 79 and threaded into the arm 85. The adjustment given to the cam roller 84, through the movement of the arm 85, changes the degree of tilt given the cradle 64 and is maintained by means of a lock nut 88. Also depending from the base member "i9 is a cradle guide 'arm 89 which supports a guide roller 9| to contact a face of the member 33. The guide roller 9| is adjustable against the member 33 in a movable roller block 92 by means of a set screw 93 passed through the member 89, all as shown. The guide roller assembly just described provides for the arcuate movement of the cradle 63 about its pivot 82.

The automatic jack 63, which is supported on the cradle 64, has as a part thereof, the revolvable base 14, previously mentioned. This base comprises a disc-like member 94 (Fig. l) from which arises an upright portion 95 and from which extends downwardly a threaded extension 96 passing through the base member 19 of the cradle 64. The upright 95 has an 'arcuate slot 97 (Fig. 3) cut therein, through which a fasten- .igpsaaaa;

a ing bolt? Mills-passed into a threaded holeiin a s'emi circular depending :extension' 99 of .a base plate l nfl (Figs. 3 and .4), said semi-circular ex- -tensionf 99 nesting itself on a semi-circular :s'h'ould'er S cut in'a face of-said upright 95. By

rotating the extension 99 in theupright95, it is possiblev to adjust the position "of a heel within thewjack'fiS about an. axis A (Fig. .3), which l passes throughthe base of the heeleand is "nor- -malto:-the 1ongitudinal aXis'55 thereof. Furthen the axis .A and the longitudinal axis of the iboltr82 lie in a common plane, so, for two positions of the base 14 (90 degrees in either direction from that which it'assumes in Fig. 3), this ad- ;justment may be thought of as being made about i the tilt axis of the cradle 64.

Supportedon the base plate I99 is anadjust- :able 'heel stop. plate IIlI over which is carried a heeLplateIOZ. pivotally connected to the stop plate at opposed points 93. The heel plate I92 biased to its upper position by .a spring I94 -and-has a plurality of holes I05 cuttherein, through which sharp pointed pins I95 pass to engage a heel *when the same is clamped in the jack. The heel plate I92 is shaped to fit -:and' support any sized heel.

"Returnin to the extension 96, the same is rotated in a bearing I01 and the base 14 is held ;in place in the cradle by a ring nut I09 which threaded onto the extension 96. A cam support Ina-is pinned to the ring nut I98 to rotate therewith and mounts a jack lift cam segment III (Figs'll and 12) whose function will be described later.

Also forming a part of the jack 63 (Figs. 3.4 and 5) is a heel clamp II2, which is automatically movable toward and away from a top lift -I -I3-:of the heel 62 first to clamp the heel in the yja'ck and to thereafter release it for automatic ejection. The heel clamp I'I2 comprises a rod -1I4 having its free end H9 serrated, as shown, .to contact the heel. This rod is mounted for rotationin a clamp arm I I1 and is retained within its'bearing I-I8'by a nut I I9. The clamp arm II1 1 is bolted to a clamp arm block IZI-which has a bore- I22 extending therethrough. provided to receive a supporting rod I23 along which. theblcck slides. As shown, the rod I23 is anchored in'the --uprightmember SI of the cradle 85 to move therewith. The block 'I2I, which 'is'shaped in cross section substantially as shown in Fig. 5,

has a second bore I24 in which'a lift pin' I25 -.s1ides. Aligned with the lift pin I25 and threaded into the block I2I as shown in Fig. 4 is a thumb screw I26 which is used to adjust the block vI2I to accommodate the Jack 63 for different sized heels. The block I2I is further provided with :=-an-exten'sion I21 (Fig. 3) which: supports a com- =..pression spring I28. The spring I28 has a rod -'I29 passed 'therethrough which extends into ami slides freely inva hole I3l in the extension I21. The'other end of the rod I29 is threaded "and isslidably passed through a hole I32 in an arm I33 bolted onto the upright I23. Lying un- '-derneath the arm I33 is a thumb nut I34 which is threaded onto the rod I29, the same being actionable to move the rod I29 downwardly and "to. carry with it a nut I35 and a washer I96, the latter bearing against the top .of the spring "128 to compress the same between it and the ex- .tension I21. Through this expedient the clamp rod II4 is held against the top lift of the heel 52- when the same --is in clampingposition in the heel jack. The strength 'of the .spring- I218,

.is of course. adjustable :by; meansccfrthefz thumb --nut.- I34.

lThe heel clamp I.I2..is automatically operated to clampg'and release-from clamping, th heel -62 through "means now'tobe'idescribed, "With fre ference to Figs-11 and 12, the previouslymentionedjack "lift cam segmentv II I is: supported to rotatewith the sheelijack. As the cam segment I I Iris thus rotated, itmoves againsta cam roller "I31 (Fig. 3) which is mounted 0n. a roller arm 2 I38 pivotally :connected to the guide :arm. 89 at .a point I39. As the beveled face I 4| of the cam --segment III is. moved .against the roller I31 the arm I39 isi'pivoted'in a counterclockwisedirec- :tion (Fig. 3) and' the :lift pin I25 is raised to bear I- against thethumb screwl26' (Fig. 4) to lift the .block .I2I and'theclamp .arm II1 and its assosciated elements vertically. '.Such lifting action is against the forces of the compression spring I28, which forces 'hold. the heel clamp II2 engaged. Thus; at an appropriate time in each revolution .of the heel 63,1the heel clamp II 2 is automatically raised to release the heel.

"Very closely related with the automatic action of the heel :clamp l i2 is the action ofv the autoinatic heel ejector'iIL-which Wi1l:now be described. Thisxmechanism comprises an ejector arm I42 (Fig. 3) which ispivotally' connected at afpoint I93 toian extensionl 4410f the revolvable base l l of the jack 63. .At its upper end the ejector arm is; is provided with a tip I45 which con- :tacts the heel'SE when the latter isejectedand, at its lower end, the arm extends into .a-section i ifi'which acts as a cam foliower. The ejector :a rm M2 is biased in;:.a1clockwiseedirection (Fig. 3) about its pivot point I43rby means of acom- -.pression spring I41. With the exception of a smallperiod of time'zduring the rotation of the jacket, the .ejectorarm I..42 held against the action: of the spring. I411.by means of an ejector .cam' I48 (Fig. 5'). zA'face 14:9 of this cam, which is rigidly attached to .the member 19, is so dimensioned as to bear against. the section I45 andthold zthe ejector .arm 142 outwardly'from thezheeluntii ejection is to beeffected. .At such time; the section I46 falls intoia' drop I5,I. (Fig. 5),

iandaunder the .action of the-spring I41, the sejectorxarm I42 is biased tdmoVe-the tip I45 against the heeluiiZ with -a snap-action and eject :the heel. This action is subsequent to the 1 re- .lease of the clamp I I 2 previously described.

All of the m'ovementsgiven to. the heel 62 by the heel feeding unit 23:.are completed in a single :cycle of operation, which cycle of operation is repeatedcontinuously through the. action-of the automatic one-revolution clutcha51. The motor '55, which. is mounted on a .motor bracket 152 (Fig. 3) to pivot with the feeding unit 23 about the .sliaft BB, drives, through a coupling I53, .a shaft ififi towhich'is keyed a worm I55 (Fig; 4). -T'he latter is enclosed inahousing I56'secu-red to the member 34 'andmeshes'with and drives :aworm gear I51 which idles freely .on the. central drive shaft 68. To this worm gear isattachjeda clutch plate. I58, illustrated in .detail in Figs. 7 and 8, which likewise rotatesfreely -about the shaft-5B, these elements being connected-by the screws 59. 'Ihe-worm,--the -worm gear and clutch plate are oil. immersed in .the housing I56 and the latter. is sealed by an -oil seal I9 I. With "further reference to Figs. 7 and.,8, .it willlbeunoted that the-clutch; plate I58 :has two holes I92 and I63'drilled ina face. thereof. These two holes are spaced "apart. .On the .asame-facexof the .clutch plate-are two lugs. -;I 64

7 'and'I65which are likewise spaced 180 apart, the lugs and the holes being positioned on diameters of the clutch plate which are normal each to the other. Lying immediately below the clutch plate I58 is a cam follower block I66 which is pinned to the shaft 68, as at I61. This block rotates with the shaft 68. In the right-hand section of the block I66 as viewed in Fig. 4, there is housed a spring pressed plunger I68 which has, as a part thereof, a pin I69 adapted to be moved, under the forces of a compression spring I1I, into either of the holes I62 or I63 in the clutch plate I56. The plunger I68 also has associated therewith a cam roller I12 which moves with it, the same being mounted for rotation about a shaft I13 and held thereon by a nut I14. A slot 15 in the walls of the follower block I66 provides for the vertical movement of the cam roller shaft I13.

Once the machine is started, the single revolution clutch 61 is automatically operated, to carry the work feeding unit through repeated cycles of operation in a continuous manner, by means of a clutch control mechanism now to be described with the aid of Figs. 9 and 10 of the drawings. Positioned underneath the worm housing (Figs. 3 and 4) is a cam block retainer I16 in which is mounted a spring biased movable cam block I11. The cam block I11 is biased to its dotted line position in Fig. 9 by means of a spring I18. This cam block carries a cam segment 19 which presents a cam face I8! to'the cam roller I12. The cam block H1, under the action of the cam roller F2, is movable from its dotted line to its full line position as shown in the figure. Here, the cam roller I12 engaged a cam roller stop I83 which is bracketed below the slidable cam assembly on a bracket I8 1. The stop I83 is bolted onto its mount I85 as shown and has interpositioned between the mount and the stop a rubber cushion I86 which absorbs the shock of the cam roller I12 as it moves against the stop I83.

When occupying their relative positions as shown in full lines in Fig. 9, the cam roller I12 has moved to a position on top of the cam segment I19 and the plunger I68 in the block I66 is moved downwardly against the forces of the spring Hi to withdraw the pin I69 from either one of the holes I62 or I63 in the clutch plate I58. When the clutch is thus disengaged, the heel feeding unit 23 is at rest, and although the motor 66 is in operation, the clutch plate I58 is the only part of the clutch which is being driven. At this time, the heel jack is in loading position to receive a heel.

The engagement of the clutch is efiected by the action of the cam block I11 which moves it to its dotted line position as shown in Fig. 9

permitting the cam roller I12 to rise vertically and pass over the stop I83. After this action has been completed, the pin I69 will pass into either one of the holes I62 or I63 to engage the clutch.

It will be observed, in all probability, that provisions must be made to release the cam block I11 Accordingly, means taking the form of the lugs I64 and I65 on the face of the cam plate I58 have been provided. As these lugs move against the head of the pin I69 they press the same downwardly against the action of the spring I1[ and carry with it the cam roller I12. The downward movement of the cam roller I12 withdraws it from contact with the cam segment I19 and the spring I18 is free to move the cam block I11 to its dotted line position. Once the cam block I11 has moved to this position, the cam roller is free to rise and pass over the cam stop I83 to engage the clutch.

It is advisable, in the operation of the machine, to provide positive means for locking the clutch control mechanism just described in its full line position as shown in Fig. 9 whereby the clutch is held out of engagement. Such means, which is illustrated in Fig. 10, is manually operated and comprises a lever I81 which is pivoted at I88 for movement on a bracket I89 extending horizontally from the retainer I16. The lever I61 carries a probe IQI which extends through a hole I92 in the retainer I16 to bear against an end of the cam block I11. When the lever I81 is positioned as shown in Fig. 10, it holds the cam block I11 against movement under the action of the spring I18 and the clutch operating mechanism is conditioned to hold the clutch disengaged. Pivoting the lever I81 in a clockwise direction about the point 588 withdraws the probe I9I and permits the cam block I11 to move to its dotted line position as illustrated in Fig. 9 whereupon the above described action of the mechanism to engage the clutch takes place.

The central drive shaft 63 is bearinged for rotation in the member 34 in a bearing I 93 (Fig. 4) and extends through the member 35 in a sleeve I64, the shaft being movable vertically in the last mentioned element. To the shaft 68 is splined the shape cam 69 and the tilt cam H by means of a key 95, each being retained in their respective mounts I96 and I91. Between these two earns, a separator I98 is interpositioned, the cam assembly being retained on the shaft by a ring nut Hi9. The shape cam 69 rides against a cam roller 261 which is mounted in an arm 282 extended from and attached to the shaft bracket 39 attached to the frame 2 I. This cam controls the movement of the feeding unit 23 toward and away from the surfacing tool 28, the shape cam 69 being urged at all times against the cam roller 29I by a spring 263 which connects at one end 294 (Fig. 3) with the member 34 and at its other end 265 with the frame 2 I.

The entire heel feeding unit lying above the member 65 is given vertical motion by means of an adjustable lift cam 266 which lies above a set screw block 261 carried on the underneath side of the member 35. The cam segment 286 is pivoted at its ends about the pins 268 and 209 and is raised or lowered by way of adjusting the effective height of the same by means of a set screw 2 I I passed through the set screw block 281. The top surface of the lift cam 286 is engaged by a cam roller 2 42 which is fixed to the block I66 attached to the shaft 68. Accordingly, as the follower 2I2 rides on the cam 266, the shaft 68 is moved vertically to give lift to the heel feeding unit, the shaft 68 sliding within the sleeve I94. The top surface of the member 35 provides a track upon which the cam roller 2l2 rides when the same is not engaging the lift cam 266.

Inasmuch as the component parts of the heel feeding unit lying above the member 35 have considerable weigh-t, a-.counterbalancing spring 213 (Fig.- 3-) is .interpositioned between the members 34-andl3fi to relieve a-rportion of the weight burdent; falling on the cam follower 2| 2. This spring isretained on a rod 2l4 which extends through-a.-- hole 2I5-inthe..member- 35 to-pass thereth-rough.: One end .of the rod is threaded intoethev member Haas-shown and a retaining washer ZIE-is-held against .the spring by means-of antad-justingnut 2 I'i. The amount ofloading on the cam follower 2I2 is. therefore adjustable by means of-the nut-.2 I L Inthe process ofloading-a .heel into the jack 63,: it is required. that the top lift portion of the samebe guided in'a'manner such that the clamp rod' twill-engage the .top lift of -.the.heel .at'a pointmarking the heel-axis. For this a purpose theaheel guide I8 is provided, the same comprisingafiber guide block 2 l8-which is mounted on an arm :2l9. The ar1n29 is bolted to the shaft bracket-39 with two bolts 22I, and 222; which are passecl through two slots 223 and 224111 the arm. The slots 223 and 224 are made wider than the bolts which-they; accommodate and accordingly-provide-for a. lateral adjustment of the fiber guide block. 2 I8.with respect to the heel 62 .as well as forfa vertical adjustment thereto. These ad justments are necessary to position the guide blockvfor various sized heels.

As -mentioned previously, one ofthe features of theinstant:inven-tion resides. in the provision of means for giving, movement or movements to a surfacing tool in timed relation to the movements of Ta heel given by a heel feeding unit movingv the heel'against'the tool. In the illustrative example, in which the surfacing tool has been shown and described as asander; this portion of the device takes the form of two movable fingers which 'act against the abrasive strip 26 to perform a function known in the art as"spooling.

In :spooling a. heel the. two breast corners at the-*topli-ft of the heel areremoved, when the heelis-cut intheheel-cutting machine'or by a subsequent operation; When the: heelis later sanded, it is -necessary that this particular sur face of the heelbe scoured and: in the prior art this .has been accomplished- .by givingto the-heel certain movements. against the sander.

In the present machine .thespooledportion of theheel,

if out in a prior operation, may. be sanded, or the sp'ooling may beaccomplish'ed completely asa sanding operation; by givingcertain movements to 'the'continuous abrasive strip 26. The mechanism' fordoing' this will now bedescribed with reference'to Figs. 2', 3, 4 and .5.

As'seen in Fig. 2, two fiber fingers 2'25 and 226 are provided which are movableagainst the inner surface of the abrasive strip 26 to move portions of the same outwardly towardv the heel feeding unit. These fingers are mounted upon vertically disposed'arms 22'Iand 228 and are horizontally adjustable within their respective arms asis shown in Fig. 4 for the finger 226 by means of a set'screw'229, the arms 22.! and 223 are'separately movable toward the heelfeeding unit in a suitable frame 23! against the forces ofseparate springs, such as the spring 232 (Fig. 4) for the arm- 228. The arm22'I is moved thusly by, a cam follower-arm 233 and. the arm 228 by a cam follower arm 234, the throw of each of these arms being' 'adjustable by separate thumb screws such as. the'screw 235'for the arm 234. The arm 233 mounts a .cam roller 236'and the arm 234 a cam follower 237. Against these two cam followers two cams J238'.and 239 are rotatedrespectively. to

impart therequired movements to the fingers 225 and.226 in timed relationship with the rotation of the heel 62 intheheelfeeding unit 23. For this purpose power is taken from-.the-central drive shaft 68, as previously stated, by the sprocket wheel and chain drive comprising the elements I5 and 16. Here, the chain 16 is passed over-a second sprocket 24I, which is keyed to a spur shaft 242 mounted for rotation in an adjustable. bracket. 243 extending, from and attached to the set screw block .201 of the heel feedingunit 23. A first-universaljoint 244, a slip joint 245 and a second universal joint 246 connect the spur shaft .242 with ashaft 241 upon which the cams 238 and 239 are.carried-. With this arrangement of the parts the cams 238 and 239-are shapedflto. give movement to the fingers 225 and 226 in .a manner such that at a given point in the rotation of theheel .62 and with its presentmenttov the sanding strip 26 the latter element will be moved. outwardly ina first instance by the finger 226 to spool the left breast corner of the heel and in asecond instance to move the finger 225 to spool the right breast corner of the heel.

Although the immediately foregoing mechanism has been described as being employed-in connection with a sander to perform the operation of spooling, it is tobe pointed out that the same is-readily adaptable to many other uses. For example, the fingers 225 and 226 maybereplacedby cutters, buffers, polishers and so forth, which will act directly against the heel to impart various different surface characteristics thereto.

Operation One of the essential features of the instant invention; resides in its automatic. operation. That is to say; once the machine is placed. in operation no manualcontrol thereof is required to start andstopits'individual cycles of operation. These are'repeated continuously and automatically, the only manual function being that of loading the heel into the heelfeeding unit. As for. thesillustrative example, the machine is placeddn operation by startingthe motors 29 and 66, the formerd-rivingthe sanding strip 26 and the latter-idling the worm gear I51 together with the clutchplate I58 on the central drive shaft 68.- Assuming' that the machine hasbeen brought to rest by the clutch control mechanism illustrated in Fig; 10, and that the lever I81 00- cupiesthe positionzshown, the lever I8! is then movedina clockwise direction to withdrawthe probe I9l which conditions the automatic onerevolution clutch 61 to be engaged; At the start of the: cycle of: operation the jack 63 will occupy a position characterized bya movement ofthe jack ina clockwise direction of from that of the position which-it takes in Fig. 1. The jack will hold this position for one-half revolution ofthe clutch plate I58 at which time the heel clamp H2 will'be-ina: raised'position. When thus conditioned andduring this period of time,

' the'operato-r feeds a heel onto the jack by placing lower I12 will ride over the cam segment I19 and the pin I59 will pass into one of the holes I62 or I63 in the plate I58 to engage the clutch. Thereafter, the central shaft 68 of the feeding unit 23 will be moved through one complete revolution, during which time the heel will receive a lifting movement under the action of the cam 206, will be tilted under the action of the tilt cam H, and will be moved toward and away from the sander 26 by means of the shape cam 69, all of these various movements being well known in the art. At a given point in the rotation of the heel in the jack 63, which occurs prior to the time the heel jack will occupy its loading position, the jack lift cam I II will be moved against the cam follower i3? and through the operation of the mechanism, previously described, the heel clamp H2 will be raised to release the heel from the jack. Immediately thereafter the section I46 of the ejector arm I42 will fall into the cam drop II of the cam I48 and the ejector 11 will operate to snap the heel out of the jack. Next, the cam roller I12 of the automatic one-revolution clutch 61 will move against the cam segment I19 and come to rest against the stop I83. These parts will hold this position to maintain the heel jack 63 stopped in loading position for one-half revolution of the cam plate I53, after which time the clutch will be engaged automatically to repeat the cycle. The machine will thereafter operate continuously, the operator loading a heel into the heel feeding unit at each period in the operative cycle wherein the jack 63 is stopped for the loading period, the number of holes 362 and I63 in the clutch plate I58 determining the length of time for which the jack E3 is stopped.

Various changes may be made in the details of construction, within the scope of the appended claims, without departing from the spirit of this invention. Parts of the invention may be used without the whole and improvements may be added while retaining some or all of the advantages of the invention.

What is claimed is:

17 In a heel making machine, a support. a pair of spools mounted on said support, a continuous strip of heel surfacing material passed around and over said spools, means for driving said spools whereby said surfacing strip is moved as a belt, a heel feeding unit pivotally attached to said support and adapted to move a heel with tilt and lift movements against an outer surface of said surfacing material strip to surface said heel, a movable finger mounted on said support for operation against an inner surface of said continuous strip of heel surfacing material, a shaft journalled for rotation in said support, a cam mounted on said shaft operative to move said movable finger against said strip, and power transfer means connecting said heel feeding unit with said shaft to rotate the same whereby said movable finger is actionable to move said strip of surfacing material against said heel in timed relationship with the movements given to it by said heel feeding unit thereby causing the heel to receive an additional surfacing action from said strip.

2. In a heel making machine, a support, a tool mounted thereon for performing an operation on a work piece, a work piece feeding unit attached to said support and pivoted for movement toward and away from said tool to carry said work piece into contact with said tool, means comprising an automatic jack for holding said work piece in said feeding unit, an automatic work piece ejector, a tiltable cradle supporting said jack and said ejector, power means mounted on said work piece feeding unit and pivotally movable therewith for driving a shaft within said work piece feeding unit, separate cam means driven by said shaft for controlling the pivotal movement of said work piece feeding unit and the tilting action of said cradle, cam means for imparting a lifting movement to said work piece as the same is moved against said tool, an automatic clutch interposed in the drive connections between said motor and said shaft for controlling the rotation of said shaft, means for controlling the engagement and disengagement of said automatic clutch whereby the said jack rotated by said shaft is maintained inoperative for a period of time equal to that required for a part revolution of said shaft and is thereafter engaged to rotate the said shaft through one complete revolution, a device for shifting an effective surface of said tool relative to said work piece supported in said work piece feeding unit, and power takeoff means from said shaft within said work piece feeding unit for driving said tool shifting device and controlling the same whereby movements are imparted to said tool in timed relationship with the movements imparted to said work piece by said work piece feeding unit.

3. In a shoe heel making machine having a tool and a work piece feeding unit adapted to move a work piece relative to said tool, an automatic jack for clamping said work piece in said Work piece feeding unit comprising a rotatable base mounted for rotation upon a shaft, a spring pressed clamp for holding said work piece between the same and said rotatable base, a cradle mounting said base and said clamp for imparting a tilting movement to both as a unit, a cam operated mechanism associated with a cam mounted to rotate with said shaft for lifting said spring pressed clamp to release said work piece from said jack and means for controlling the rotation of said shaft whereby said rotatable base of said jack is held inoperative for a portion of one revolution of said shaft and is thereafter moved through one complete revolution, said cam operated mechanism being made operative to release said clamp from engagement with said work piece at a fixed period of time prior to the completion of said full revolution.

4. In combination with a shoe'heel making machine having a tool and a work piece feeding unit adapted to move a work piece relative to said tool, a device for shifting an effective surface of said tool relative to said work piece, a movable arm mounting said device, cam means for moving said arm, and means for driving said cam to move said arm comprising a power takeoff from said work piece feeding unit connected with said device to move the effective surface of said tool relative to said work piece in timed relationship with movements imparted to said work piece by said work piece feeding unit.

5. In a shoe heel surfacing machine having a continuously moving belt and a work feeding unit for moving a shaped heel against an outer surface of said belt with rotational motion to cause said belt to engage and pass over certain surfaces of said shaped heel, the improvement comprising first and second displaceable fingers mounted for displaceable movement normal to the path of the belt against an inner surface of said belt, and means for displacing said first and said second fingers as aforesaid sequentially in timed rela- 13 tionship with the rotational movement of the said shaped heel.

6. In a shoe heel surfacing machine having a continuously moving belt and a work feeding unit for moving a shaped heel against said belt with rotational, reciprocating and lift movements, the improvement comprising a tiltable cradle mounting a turning shaft and a jack attached thereto in which said heel is supported for rotational movement, means for tilting said cradle in timed relationship with the rotation of said heel to carry the same against a certain given contour of said belt, a finger movable against said belt, and means operating .to move said finger in timed relationship with the rotation of said heel to cause the belt to assume a different contour and give to said heel a shape characteristic other than those originally possessed by it upon its introduction into said feeding unit.

'7. In a shoe heel surfacing machine, having a continuously moving belt and a work feeding unit for moving a shaped heel against an outer surface of said belt with rotational motion to cause said belt to engage and pass over certain surfaces of said shaped heel, the improvement comprising fingers mounted respectively on either side of a station occupied by the work when in engagement with the belt and each positioned for movement againstthe inner surface of the belt, and means operable in timed relationship with the rotational movement of said shaped heel for manipulation of the fingers against the inner surface of the belt, whereby they impart to the belt momentarily a contour other than that assumed by the belt in traveling its normal path.

8. In a machine for operating on a work piece to give a desired shape and having a support and a tool on the support, the improvement comprising a work feeding mechanism having a frame mounted for reciprocation on the support, a cradle pivotally supported in the frame, a shaft journalled in the cradle along an axis normal to the pivot of the cradle a clamp on the cradle in alignment with the shaft constructed and arranged to hold a work piece to the shaft, driving mechanism for the shaft, means connected to said driving mechanism, and thereby driven in synchronism with the said shaft and the work piece held thereto, for tilting the cradle on the pivotal support, means also connected to said driving means and operating in synchronism with said shaft for reciprocating the frame on the support, and means also connected to said driving mechanism for changing the position of an effective surface of said tool in synchronism with the rotation of said work piece.

JUSTIN P. QUIRK. LUDWIG G. P. HAFNER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 2,057,290 Bradbury Oct. 13, 1936 2,064,476 Johnson Dec. 15, 1936 2,123,269 Ball July 12, 1938 2,352,690 Clausing July 4, 1944 2,359,488 Ponder Oct. 3, 1944 FOREIGN PATENTS Number Country Date 824,362 France Feb. 7, 1938

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