US2309141A - Hat brim pouncing machine - Google Patents

Description

Jan. 26, l943. f P. scHULTZE V HAT BEIM POUNCING MACHINE 5 Sheets-Sheet 1 Filed March 22. 1940 l I l lll' 5 W w w m, .4 l .RL Y, uw. jow m 4 .mc E5 /T W T m ,l azz a 6 va 2 c 52 a n .i 2 a 1 .a a/J s y 2 2 w Y z Q.

lili Jan. 2s, w43. P. SCHULTZE 2,302,141

HAT'BRIM POUNCING MACHINE ATTORNEY Jan. 26, 1943.

F. SCHULTZE HAT BIM POUNGING` MACHINE Filed March 22, 1940 5 Sheets-Sheet 3 ATTORNEY -Fa- 25, 1943- P. scHULTzE .y HAT ERIMA POUNCING' MACHINE 5 shets-sheet 4 Filed March 22, 1940 UWMQ E W m a TM ma mgm Jan'. '26, 1943.

HAT BRIM Filed Mami 22, 1940 P. SCHULTZE POUNCING MACHINE 5 Sheets-Sheet 5 Patented Jan. 26, 1943 TES HAT BEIM POUNCING IVIA'CHINE Paul Schultze, Danbury, Conn., assigner to Doran Brothers, Incorporated, Danbury, Conn., a corporation of Connecticut 39 Claims.

This invention relates -to machines` for iinishing, as by pouncing, or sandpapering, the brims of hat bodies.

One of the objects of this invention is' to provide a hat brim pouncing machine that will be of high eiiicicncy and of high precision in action` compact and durable in construction, and of ease and facility of control and operation. Another object is to provide a hat brim pouncing machine in which the advantages of higher surface speeds for the operating yor pouncing tools than has heretofore been possible may be achieved in a safe, dependable and Practical way. Another object is to provi-de mountings, drives and controls for the brim operating tool or tools capable of dependable and long-sustained operation at high speeds. Another object is to provide a brim pouncing machine with operating tool or tools and a hat body support and feed that will be capable of producing better and more eilicient results than has heretofore been possible and capable of control and operation on the part of an operator, as, for example, in the insertion or replacement of a hat body, that Will be simpler and more e-flicient `than in prior practices and that require less skill or manual attention or supervision over prior expedients, Another object is to carry out this last-mentioned object with mechanism that will be simple and compact and constructed and operated so as to afford the operator complete safety and also to insure the desired operation upon the hat body Without chance of damaging the latter.

Another object is to provide a brim pouncing machine in which the upper side of the brim ,l

may be with complete safety to the hat body itself pounced or nished .throughout its entire radial dimension, -that is, up to the junction between the brim and the crown, without danger of injury to the crown portion of the hat body. Another object is to provide a brim operating machine in which certain advantages in which giving the brim tool a motion in a closed path may be successfully achieved and may also be made dependably and` successfully effective throughout the radial extent of the brim without endangering or harming the crown of the hat in the region where it joins the brim. Another object is to provide in a brim pouncingr machine a mechanism, such as a mount and drive, to make possible the functioning of brim pouncing pads, moving in a closedv path, at such high surface speeds relative to the brim being operated upon, as will be feasible for sustained operation and as will produce commercially acceptable and superior results. Another object is to provide such a high speed apparatus with a safe and dependable hat support and brim feed, with dependable means for feeding or renewing the tool material, such as abrasive strip or sandpaper, and capable of reliable action andv control under the conditi-ons of high speed, and to insure safety of construction and operation.

Another object is in general to provide an improved brim pouncing machine, to facilitate manufacture and assembly, and tol achieve greater reliability of construction and performance and thus to achieve improvedY results at less' attendant cost, such as maintenance, and the like. Another object is to provide in a machine of the above-mentioned character simple and dependable means for controlling, regulating or adj-usting the action of various parts. Another object is to provide dependable and easily controllable means for replacing or feeding the operative material of thetool or tools, such as-abrasive strip or sandpaper..` Other objects will be in part obvious or in part pointedl out hereinafter.

The invention accordingly consists in the features of construction, combinations of elements, arrangements of parts and inf the several steps and relation and order of each of the same4 to one or more of the others, all aswill be illustratively described herein, and thel scope of the appli'cationr of which' will be indicated inA the following claims.

In the accompanying drawingsV in which is shown by way of illustration one of the various possible embodiments of my invention,

Figure l isA a side eleva-tion of the complete apparatus with part of the enclosing casing removed, certain partsY being broken away and others Is hown in section in order to show certain features of the construction more clearly;

Figure 2 is a central'vertica-l longitudinal sectional view of the Complete machine; Figure 3 is a view on an enlarged scale, as seen substantially along the line 3 3" of Figure 1, showing portions of the feed mechanismfor the abrasive strip material;

Figure 4 is a horizontal sectional view, as seen along the line 3L-il of Figure l; Y

Figure 5 is a horizontal sectional View along the line 5-5' of Figure 3, showing more clearly certain of thel mechanismy for assembling the housing or casing, andI FigureV 6` is a transverse or vertical sectional view on an enlarged scale, as seen along the line 5'6L of Figure 4 showing certain fea-tures? of the padconstruction.

Similar reference characters refer to similar parts throughout the several views in the drawings.

Referring rst to Figures 1 and 2, I provide a suitable base or standard i9, preferably of round cross-section, and provided, as at Il, with suitable flange means, or the like, whereby it and the high speed apparatus carried by it may be securely anchored to the door, and carrying at its upper end suitable frame means which are preferably built up as, for example, by two upstanding curved plates i2, i3 (Figures 1, 2 and 4) of suitably heavy material of good strength like steel, their radius of curvature, preferably that of a circle less than the radius of the base I0, giving them great rigidity against distortion or bending. Plates l2-I3 are secured as by screws or bolts i4 at their lower ends to correspondingly curved flanges l5, il that project upwardly from the upper face of the base ID, whereby frame plates |2-i3 are rigidly supported in upstanding parallel relation and preferably arranged concentrioally with respect to their curvatures and the center of the round base I0. In thus positioning them, they are preferably located so that the space between their right-hand vertical edges, as viewed in Figures 1 and 2, is greater than the space between their left-hand vertical edges.

At their upper ends the frame plates i2-I3 support and have rigidly secured to them, as by screws or bolts I3, a frame part 2D, preferably in the form of a casting, the latter being suitably shaped or flanged (see Figure 3) to intert with the upper ends of the frame plates l2-l3 and to form with the latter a strong and rigid upward continuation of the built-up frame structure.

Frame part supports the outer race (see Figure 2) of a combined thrust and radial antifriction bearing 2l whose inner race supports, as by a bushing, as shown, the lower end of a main `operating shaft 22 provided with eccentrics as later described. At its upper end shaft 22 is rotatably supported by a companion combined thrust and radial antifriction bearing 23 whose inner race is secured to the shaft and whose outer race is secured in or carried by a frame part 24 which is preferably in the form of a casting and has two horizontally spaced downwardly extending parts 25, 26 (Figures 1, 2, 3 and 4), preferably curved and cross-ribbed, as appears better in Figure 4, to provide strength and rigidity. Side parts 25, are of sufficient downward extent to meet correspondingly spaced upward extensions 21, 28 (Figures 1, 2, 3 and 4) of the frame part 2i), these meeting pairs of parts being rigidly secured together as by screws or bolts 3U.

The operating shaft 22, driven preferably at high speed, as is later described in detail, actuates two tools or tool structures, generally indicated by the reference characters 3i and 32, being preferably, as is later described in detail, in the form of suitable abrasive material suitably backed up preferably as by a suitable resilient material, like rubber, for operation upon the respective sides of the brim B (Figures 1 and 2) of a hat body generally indicated by the reference character 33 and supported and fed in a preferred manner later described. Preferably, the tools 3l, 32 are actuated, preferably in opposite directions relative to one another, so that their operating faces move in a closed path within their respective planes; in order, however, to achieve the advantage of such a path of motion,

the linear velocity should be of a high order of magnitude and in brim pouncing machines heretofore proposed it has been impossible to achieve the magnitude of velocity desirable for accomplishing high quality and high eiciency of action and result. In accordance with certain features of my invention, however, I am enabled to achieve velocities of motion of a magnitude and in a manner to make commercial achievement of high quality of brim pcuncing feasible.

A form of mechanism for giving the tools 3|, 32 sustained high velocity of motion in closed paths is shown in the drawings and may comprise the two above-mentioned eccentric portions 22a and 22b of the operating shaft 22 coacting, respectively, with lower and upper tool carriers, generally indicated at 34 and 35, and related coacting parts later described in detail.

Tool carriers 34-35 are preferably made of a suitable alloy having lightness and strength, such as a magnesium alloy, and With the parts they respectively carry, including the tools, they are preferably of generally similar construction.

Thus, carrier 35 may comprise a sleeve-like part 36 (Figure 2) within which is a bushing-like member 3l suitably stepped at its two ends to receive the outer races respectively of two combined thrust and radial antifriction bearings 38, 39 whose inner races are carried by or mounted upon the eccentric portion 22b of the main shaft 22, that eccentric portion being conveniently, and, as shown, formed out of two axially spaced parts of the shaft.

In the illustrative embodiment, eccentricity of the portion 22b is M3", as is also the case with the other eccentric portion 22a, these two p0rtions being spaced from each other Extending to the right (Figure 2) from the sleeve part 3S, the carrier 35 has an extension 4l which supports the tool 3| and extending to the left and diametrically opposed to the extension 4| is a sleeve-like extension 42 in which is fitted and secured, as by a pin 43, a cylindrical member 44 which is preferably constructed to be strong and Wear-resisting but relatively light, preferably taking the form of a relatively thin-walled steel tube. It is of sufficient extent in a direction toward the left (Figure 2) to be slidably received within a bearing member 45. Bearing member 45 is preferably lined, as indicated in Figure 2, with suitable bearing material, such as a selflubricating material, as indicated at 4G, and it may also be constructed to accommodate suitable means, for retaining a lubricant, such as felt washers 47. With the operating shaft 22 driven at a suitably high speed, illustratively 3600 R. P. M., the member 44 oscillates or slides back and forth relative to the bearing member 45 at high surface speed and at a high rate, partaking, in the illustration, of '7209 strokes per minute. But because of the circular motion of translation which the eccentric 22b gives to the sleeve part 35 of the carrier 35, bearing member 45 is arranged to oscillate about a pivot preferably provided by a stud shaft 48 which extends through a lateral extension 45El (see Figure 4) of the bearing block or member 45 and which is rigidly supported in a manner later described.

Carrier 34 (Figures 1 and 2) is, as above noted, constructed substantially similarly as carrier 35; it has a central sleeve portion 50 from which extends toward the right an extension 5I which carries the tool 32, and a sleeve-like extension 52 (Figure 2) toward the left in which is secured as by pin 53, a steel tube member 54, like member d4, slidably guided in a bearing member 55, like the member 45, and mounted as by the sleeve-like bearing extension 55 to oscillate about the upright shaft 48. Shaft 48, as better appears in Figure 4, may be made tubular, as of steel tubing.

In the preferred arrangement the upper tool carrier 35 is, by the earlier above'described assembly to the operating shaft 22, held against movement in a direction lengthwise of the operating shaft 22, the rigid support for the latter, provided by the above-described vertically spaced bearings 2i and 23, in the lower bearing frame 2U and the upper bearing frame 24, permitting it dependably to take up and dissipate to the frame structure moments of force or thrust, such as could be transmitted to the shaft by the reaction of or pressure exerted by the tool Si, it being noted that the tool carrier 35 is in turn and to better transmit such thrusts, carried by the shaft 22 by the bearings 38, 39, which are of substantial spacing lengthwise of the shaft. Thus, rigidity and precision and integrity of structure are dependably maintained. The tool carrier 34 with its tool 32 is, however, preferably arranged for controllable movement, axially of the shaft 22 but in a manner to insure the dependable transmission to the shaft 22 and to the supporting frame structure moments of thrust or force due to the reaction of or pressure exerted by the tool 32.

A preferred arrangement for so mounting the tool carrier Sil comprises the above-mentioned sleeve part i] which is preferably considerably elongated axially to provide an axially long bearing relative to an internal sleeve 56 also of substantial axial length and which is carried by the axially spaced eccentric portions 229- of the shaft 22 by means of correspondingly axially spaced combined radial and thrust antifriction bearing 51 and 58, the inner races of which are fixed to the crank portions 22a and the outer races of which are fitted and xed internally of the sleeve 56.

Sleeve 5t is preferably made of material like steel and preferably its external cylindrical face is machined to provide two axially spaced bearing surfaces adjacent the respective ends of the sleeve 5f; internally of the sleeve part 59 of the carrier 313 I preferably provide axially long bushings 69, 65 of a suitable bearing material, such as a self-lubricating or so-called oilless bushing material for coaction, respectively, with the justmentioned external bearing surfaces at the ends of the internal sleeve 55.

Accordingly, during drive of the shaft 22V, the inner races of the upper spaced bearings 38, 39, related to the upper tool carrier 35, rotate with the eccentric portion 222b of the shaft 22 but relative to the non-rotating parts St, 3l of the upper tool carrier which partakes of motion of translation that is in a closed circular path as far as the parts 355-3? are concerned, while the inner races of the lower spaced bearings 5l, 58 of the lower tool carrier Se, rotate in a similar way with the eccentric portions 22a of the shaft relative to the non-rotating internal sleeve which is given a motion of translation in a closed path that is circular; a similarmotion is by the sleeve 5B conveyed to the sleeve part 5@ of the tool carrier 34 but during such actions tool carrier 34 may be moved in an axial direction relative to the axially immovable internal sleeve 5S, thus to vary the distance between the faces of the two tools 3l 32, the large coacting bearing surfaces between the internal sleeve 55 and the bushings 6e?, 5t and their axially spaced relationship insuring not only long wear but also freedom from play and dependable transmission to the shaft and through the latter to the frame structure of thrusts caused by or at the tool 32.

The -two tool carriers, being thus moved in opposite phase relations, are, with respect to each other, preferably dynamically balanced in any suitable way. Preferably, to make up for the axially elongated slidable bearing arrangement provided between the internal sleeve '55 and the sleeve part 50 and the resultant weight of these parts, as compared to the shorter axial lengths related to the upper eccentric 221, member 3'! is shaped or machined to be of substantially the same weight with its tool carrier 35, as is the internal sleeve 56 with its tool carrier 34, related to the lower eccentric 22a, thus to substantially equalize the masses or weights of the aggregate entities respectively set into and maintained in motion by the two eccentric portions 22a and 22b and thus at the high speeds of operation to counteract tendencies to set up couples or forces creative of harmful stresses or vibration. With the two eccentric portions 22a and 22h operating 180 out-of-phase from each other, the masses respectively moved by them move substantially in opposite directions and the moments of force they respectively set up, being very substantial at the high velocities of motion, substantially counteract and neutralize each other, with negligible or minimum effect so far as the apparatus as a whole is concerned.

For a preferred embodiment for effecting safely high speed of drive, at say 3500 R. P. M., l prefer to employ an electric motor 62 (Figures l and 2) mounted with its shaft 53 extending vertically and preferably in substantial alinement with the operating shaft 22; preferably, motor 52 is accommodated between the curved upright frame plates |2-i3, being entered in between them through the wider opening or space at the righthand edges thereof and being substantially snugly accommodated therein and secured thereto as by a composite bracket til which preferably comprises a plate-like member 65 bridged across and Vinternally interfitted withthe frame plates IZ-IS and secured thereto as y bolts 55, thus also strengthening the frame structure l2--i3. Plate-like member G5 lis provided with vertically extending ways 6l' with which is slidably interiitted a suitably conformed portion. of a companion plate-like part 65 which is secured to the motor frame 62 as by screws lf3, the two parts 65 and E5 being clamped together, as by a clamping screw il, this arrangement permitting adjustment of the motor 52 in a vertical direction.

At its upper end motor shaft 53 carries a pulley T2 which, through a suitable belt, preferably a V-shaped rubber belt i3, drives a pulley 'M secured together with a companion pulley 15 and supported for rotation on a downwardly projecting stud shaft 15 carried by a leftward extension (Figures 1 and 2) of the lower bearing frame 2Q. Pulley 75, through a suitable -belt TI, also preferably a V-shaped rubber belt, drives a pulley lt secured to the lower otherwise free end of the operating shaft 22.

Stud shaft T6 that supports the double pulley- 'i4-'l5 is preferably adjustably mounted so that the tension of the belts l, 'il may be fixed or adjusted. Conveniently, for this purpose, stud shaft 76 has an upper portion '56a that is slidably received in a slot in the extension of framek 2i),v slot 8B extending in the; direction'of the line joining the axes of shaft 1S and shaft 22, and upon fixing the position of stud shaft i5 it may be clamped in place as by a clamping nut 8| between which and a collar 82 on the stud shaft the slotted frame portion becomes clamped.

By thus transmitting the drive from motor shaft 63 to the operating shaft 22, I am enabled to achieve a number of advantages. With a motor of fixed speed characteristic, I am enabled by appropriately varying the pulley diameters to achieve a different rate of drive of operating shaft 22. Also, I am enabled substantially to isolate the motor and the operating shaft and its related mechanisms from each other, thus avoiding the imposition upon the operating shaft and its connected parts of strains or stresses or vibrations inherent in the motor or its operation and vice versa. Also, I am enabled thereby to isolate from the high speed brim operating mechanism the drive of other parts of the apparatus, such as the feed of the hat brim between the two operating tools 3|, 32, as is later described.

With the operating shaft driven as above described, thus giving the adjacent faces of the operating tools 3|, 32 motions of translation at high velocity but in closed paths within their own respective planes, the drive need not be interrupted to insert or replace a hat brim between the two operating tools or, as is later pointed out,

to effect a feed of the abrasive strip which is the preferred form given the operating parts of the two tools. rIhe latter operate upon the brim B while pressed toward the respective sides or faces of the brim with a suitable pressure, and

where, as in the preferred form, the lower tool g carrier 34 with its tool 32 is movable axially, I prefer to apply to the tool carrier 34 suitable means for urging it and hence the tool 32 upwardly; such means may comprise a spring S3 interposed between the extension 5| of the tool carrier 34 (Figure 2) and a suitable part of the lower bearing frame 20, the spring 83 by its tendency to expand urging the carrier 34 to slide upwardly with its sleeve part 59 relative to the axially immovable internal sleeve 69. Preferably, the action of spring 83 is adjustable and this may be arranged by fitting its lower end over the upper end of a threaded stud 84 threaded into the frame part 29 and provided with a knurled flange 85 by which its axial position, and hence the compression of the spring 83 adjusted, a lock nut 8B being provided to x or set the adjustment.

To effect separation of the tools 3|, 32, I provide means, preferably manually actuated, to effect movement of the movable tool carrier, il-

lustratively tool carrier 34, acting in opposition to spring 03. This means preferably comprises a handle 87 (Figures l, 3 and 4) projecting normally in a general upward direction to one side of the tools 3|, 32 where it is thus located for convenient manipulation by the operator, handle 8l' being secured at its lower end to a shaft 88 projecting from and rotatably carried in a suitably shaped portion 95 of the lower bearing frame 2D and secured, as onto the shaft 88, to swing or move with the lever 8l, is a toothed or rack member 9| which meshes with the toothed or rack portion 92 of a lever 93 rotatably mounted on a stud shaft 94 projecting from the frame part 20. At its outer end lever 93 has pivotally connected to it a link 95 whose upper end slidably carries a ball member 96 that rests in a socket part 91 at the outer end of a U-shaped yoke, generally indicated by the reference character 98; a nut |00 with a lock nut |0| (Figure 3) permits adjustment of the effective length of link 95.

The two sides or arms 9.*3a and 98h of the yoke 98 (see Figures 4 and 2) extend toward the opposite side of the upper frame part 24, passing directly over the tool carrier extensions 52 and 5|, respectively (Figure 2), and at their ends are pivoted by a suitable stud or pin |02 (Figure 3) to the opposed sides of the part 26 of the upper bearing frame 24. The tool carrier extensions 52 and 5|, where they underlie the yoke arms 98a and 98h, respectively, are suitably recessed to receive wear plates |03 and |04, respectively, and the two yoke arms 98a and 90b where they overlie these carrier extensions 52 and 5|, respectively, have pivotally attached to them shoes |05 and |06, respectively, whose under faces are Preferably provided with suitable self-lubricating alloy, such as is employed for so-called oilless bushings. Spring |08 biases yoke 98 upwardly (Figure 3).

Accordingly, if handle or lever 81 is swung in clockwise direction, as viewed in Figure 1, the rack 9| rotates lever or link 93 in counter-clockwise direction, through its engagement with the rack 92 thereon, thereby pulling link 95 (Figures 1 and 3) in downward direction, and swinging yoke 98 in clockwise direction (as viewed in Figure 3) about its pivot support |02 and against the action of spring |08 (Figures 1 and 2), this movement of the yoke bringing its Contact shoes |05 and |06 (Figures 2 and 3) into engagement with the wear plates |03 and |04, respectively, of the moving tool carrier 34, and thereafter sliding the latter downwardly relative to the internal sleeve 45 along the axis of the operating shaft 22.

The range of resultant motion in downward direction that is given to the tool 32 is suflicient to achieve a separation between the adjacent tool faces sufficient t0 remove the brim of a hat body and replace it by another. Preferably, the tool moving mechanism is constructed so as to lock or hold the movable tool in its position of tool separation and preferably, for this purpose, link 95 and the rack lever 9S (Figure 1) are proportioned and related to function as a pair of toggle levers, the range of counter-clockwise rotary movement of lever 93 being suilicient to bring the pivotal connection thereto of link 95 over to the right-hand side of the axis of rotation of rack lever 93, thus locking the parts in lowermost position against the action of spring 83. To restore the displaced tool 32, lever 81 is simply moved in reverse direction, namely, it is swung in counterclockwise direction and as soon as the pivotal connection between links 95 and 93 passes to the left of the axis of link 93, the retrograde or upward movement of the parts to operating position is aided by the action of spring 83 on carrier 5| and spring |08 on yoke 98.

During such actuation of the movable tool its high speed of actuation, as above described, continues; as the tool carrier 34 slides with its sleeve 5] (Figure 2) downwardly relative to the internal sleeve 5E, or upwardly, as the case may be, the bearing member 55 (Figure 2) in which the tube extension 54 of the tool carrier continues to reciprocate pai-takes of a corresponding downward or upward sliding movement relative to the stationary stud shaft 17.8. The latter is fixed to a bracket |||l secured as by screws Il! to extend toward the left of the lower bearing frame 20. To insure greater rigidity for the stud shaft 48, aside from its anchorage in the outer end of backet HQ, the latter has similarly anchored tov it a member ||2 substantially identical to the stud shaft IIS, being spaced from the latter but extending parallel to it, with the upper ends of the two members t3 and ||2 rigidly tied together by a cross-piece II3. Thus, any tendency of the stud shaft |33 to flex is resisted not only by its own rigidity and that of its mounting, but also by that of the companion member H2. With such an arrangement, the major portions of the bearing members l5 and 55 (Figures 1 and 2) extend between the two parallel members I3 and IIZ and, if desired, and as indicated in Figure l, the members 45 and 55 may be externally shaped or cut away to insure ample clearance between them and the member 2, as they partake of oscillation about the axis of their supporting member 48. Illustratively, part I8 is tubular and part ||2 solid.

Also, it will be noted that the rapidly moving parts or tool carrier extensions 'I and 54 thus become confined laterally between the two upright members I3 and H2 and above and below by the cross-piece I I3 and the heavy bracket I IB, respectively.

With such control of the separation or approach of the two tools, the brim B of a hat body 33 (Figures 1 and 2) may be quickly inserted between the faces of the two tools or removed therefrom; to facilitate replacement of the hat body and a feeding action upon the latter to cause the brim to be progressed during the operation thereon of the two tools, I prefer to employ a mechanism and arrangement better shown in Figures 1 and 2. At the lower part of the apparatus I provide a housing-like member I I5 having a top wall H5a from which extend downwardiy and outwardly, in suitable curvature, opposed side walls I |5b and I I5c and an end wall HEd, for purposes later described. Extending upwardly from the upper wall |I5aL is a standard or column, preferably in the form of a tube I I6, suitably secured at its lower end to the member IE5 as, for example, by interiitting it with a suitable internally flanged aperture in the member I I5 and locking it in place as by a set screw I Extending through the column II@ and rotatably supported thereby is a shaft IIB, as by anti-friction bearings |23 and I2I, suitably mounted at the respective -ends of the column I I6 and acting preferably also as thrust bearings, thus to hold the shaft H3 against axial movement relative to the column IIS.

At its upper end shaft IIB carries a means for engaging with the inside of the crown C of the hat body, and in a preferred form it comprises a metal hub |22 secured to the shaft IIB to be rotatable therewith and having a member |23, like a tire, extending peripherally about the hub I 22, being made preferably of a material that can engage the felt or other material of the hat body with a good grip free from substantial slippage and preferably also being yieldable or resilient; a peripheral member |23 made of rubber, preferably of substantial radial dimension, as indicated, and of an outside diameter approximating the minor axis of oval hat crowns to be operated upon, I have found to give good results. Itis secured to the metal hub |22 in any suitable way, as by cementing, and to avoid exposing any rough edges or rough parts of the construction I preferably surmount the rotary structure I22-I23 by a curved cap IZIi which conveniently is in the form of a segment of a sphere and which conveniently also is internally threaded,

as at |24a to serve as a nut to clamp the hub member |22 onto the shaft H8, though I prefer also to employ other means, such as a key, to insure that the hub |22 partakes of the same rotation as does the shaft IIB.

.The peripheral face of the yieldable rotary member |23 is preferably frusto-conical and illustratively may partake of a 12 taper relative to its axis of generation or rotation. Shaft |I8 with its supporting column IIS and the housinglike member H5 are supported as a unit from the lower portion of the apparatus but in such a way that the hat-engaging member |23 may move toward or away from the outer or front edge portions of the tools 3|, 32 and this I preferably achieve by providing a pivotal connection or support for the housing part H5 with respect to the frame structure of the apparatus. This pivotal support may comprise two laterally spaced brackets |26 and |21 (Figures l and 2) having curved portions to seat externally against the curved faces of the frame plates I2 and I3, respectively, to which they are secured as by bolts or screws |28 and |29, respectively, the two brackets presenting toward thev front of the machine (the right as seen in Figures 1 and 2) spaced but alined eyes |23a and |2'Ia, respectively, for the reception of pins or bolts |30 and |3| to form pivotal connections with brackets |32 and |33, respectively, that are secured to and internally of the opposed side walls ||5b and III'c of the housing-like support H5. Y

These parts are so proportioned that when they are swung as a unit in counter-clockwise direction about the axis of the just described pivotal connection and to the position shown in Figures 1 and 2, the substantially horizontal plane of the lower edge of the frusto-conical face of the hatengaging member |23 is just about coincidental with or slightly below the plane of the under face of the upper tool 3| so that, with the lower tool 32 moved into lowermost position, as above indicated, a hat body appropriately related to the member |23, as is later described, has Vits brim carried into the space between the separated tools, while if swung in reverse direction, after separation of the tools, a hat body has its brim removed from in between the separated tools.

C'oacting with the member |23 is a table-like support |35 carried by the column H6, preferably adjustably, so that its upper face |351, which is substantially f|at, may be given an angle suited to such factors as the angle of taper of the crown-engaging part |23, the angle between the crown side and the brim, or the like.

Table member I 35, aside from the top Wall or top face portion |3521, is preferably constructed to have depending skirt-like anges or walls, such as an end wall |35b, which may be substantially straight and which preferably extends at right angles to the longitudinal horizontall axis of the apparatus and a single wall |35c curved or shaped to comprise opposed side walls and an opposite end wall; the wall p0rtion |35c may be, in plan, substantially semicircular. With such preferred construction, the mounting of the table |35 to the column I It and the mechanism for adjusting its angle, may be embodied within the hollow under side of the member I 35 and is Ipreferably constructed to provide for up and down adjustment of the -table |35 relative to the column IIS and also for adjustment of the angular relationship therebetween.

A suitable mounting means of this character may comprise a sleeve-like bracket |36 through which the column ||6 extends, bracket |35 being split and provided with a clamping screw |31 so that the position of the sleeve bracket |35:` lengthwise of the column ||6 may be set as desired, as well as, where necessary, the angular relationship thereof about the axis of column ||6 determined. Sleeve bracket |35 is provided with trunnions |38 preferably one on each side of the bracket; |36 and hence one on each side of the column H6, to receive the split sleeve portions |40a of two brackets |40 which extend along and underneath an internal rib |352 to which they are secured as by screws |4I, the split sleeve portions |40a having clamping screws |42. By this arrangement the angle of tilt of the top face |35a of the table |35 about the axis of the trunnions |38 may be adjusted. The left-hand central portion of the table |35, as seen in Figures 1 and 2, is, of course, suitably shaped to accommodate the column H6 and to provide adequate leeway for such adjustments as have just been described.

A preferred and illustrative adjustment of these parts is shown in Figure 2 from which it will be seen that the plane of the table face |35a inclines downwardly toward the right when the parts are in position to present the brim B of the hat between the two tools, the plane of the top face, if extended toward the left, just about intersecting the extreme left-hand lower edge portion of the member |23. With a hat body resting upon the table face |35a and with the crown C thereof taking over the driven element |22|23, the major portion of the brim of the hat rests upon the table face |35f'- but at such an angle as to present the junction between brim B and crown C where the latter is internally engaged by the element |23 to the lower edge of a member |44 that coacts with the rotary element |22|23 to fix the position of that junction relative to the two moving tools and to maintain such position of the junction fixed as the hat body is rotated by the element |22|23.

Member |44 is preferably constructed in the form of a bar of rectangular cross-section, as is better shown in Figure 4, and is preferably rigidly supported at the outer ends of two parallel rods |45, |46, whose inner ends are supported in suitable bores 25a and 23EL of the upper bearing frame 24 (Figures 4 and 5), where they are secured or anchored in any suitable way.

The inner face |44a of the bar-like member |44, preferably extends vertically (Figures 2 and 4) and is positioned so that its plane is just about coincident with the edge portions of the upper tool 3| when the latter is in its extreme right-hand position, while the horizontal plane of the lower or under edge of member |44 is substantially coincident with the horizontal plane in which the under face of tool 3| lies or operates. At a middle portion of its righthand' face, as viewed in Figures 2 and 4, the barlike member |44 is cut or milled away, as at |44", preferably along a curved plane which is tangent to the right-hand edge of the upper face, as at the point a: (Figure 4) and which is tangent to the left-hand edge of the lower face, as at y, the plane of cutting or milling being virtually cylindrical. It is against this curved face |44b that the band or lower portion of the crown C of the hat body (Figures 1 and 2) is pressed by the rotating element |22, |23, and since at the point y Ithe thickness of member |44 is negligible or just sufficient to avoid presenting a sharp or cutting edge, and since the left-hand face |44a of the member |44 is substantially at the limit of the stroke of tool 3| in a direction toward the right, the entire radial dimension of the upper face of the brim B is thus exposed to the scope of operation of the tool and maintained so exposed as the hat body rotates under the action of the rotary element |22, |23, for the same pressure exerted by the yielding rotary feed element |23 to grip and rotate the hat; is effective to press the band portion of the crown always against the curved face 44h of the member |44, thus insuring that the entire radial dimension of the brim B, as the latter progresses around and around, is exposed to the operating surface of the tool 3|.

While the upper tool 3| is operating on the upper side of brim B, the lower tool 32 is operating upon the under side of the brim, being pressed upwardly by the action of spring 83 (Figures 1 and 2) by a pressure which may be determined by adjustment of the spring 83 as by the adjusting elements 84-85-86 (Figure 2).

Preferably, the extent to which spring 03 urges the lower tool 32 through its tool carrier 34 upwardly, is limited to a sufficient extent to prevent the two tool faces from operating against each other in the absence of a brim B therebetween. Such limiting action may be achieved by setting the uppermost position of the yoke 98 (Figures l, 2 and 3) with the handle 01 in uppermost or normal position; this may be accomplished by setting the position of the ball member 06 (Figure 3) relative to the link 95 by means of the adjusting nuts |00-!0|. Thus, as appears clearly in Figures 2 and 3, it will be noted that the under faces of the shoes |05, |05 of the yoke 98 are at such a position as to permit a slight further upward movement of the tool carrier 50 under the action of spring 83 (Figure 2) before the wear plates |03 and |04 are brought into contact with the shoes |05, |06. Thus, though the brim B be removed from in between the tools 3|, 32, as viewed in Figure 2, the tool 32 is permitted to approach tool 3| beyond the position shown in Figure 2 but limited by the leeway between wear plates |03, |04 and the yoke shoes |05, |06, respectively.

With the tools actuated preferably at such a high speed as noted above, the cutting speed of any abrasive particle on the tool faces is high and is substantially the same as that of any other point or particle on the tool face, with the result that a uniformity of pouncing action throughout the radial extent of the brim B surpassing prior practices is achievable; the brim is operated upon on both sides throughout its entire radial extent and it might be noted that it has heretofore been impossible to achieve action at those regions of the upper brim side closely adjacent the crown. The rotary pressure and feed. element |23 takes part in assuring these actions, maintaining that portion of the brim that is between the two tools always in proper relationship to the latter and due to its relatively slow rotary movement it insures the dependable steady presentation of successive portions of the brim into the operative region between the two tools.

The rotary feed and pressure element |23 is rotated at a speed to give its peripheral hat-engaging surface a relatively very low surface speed; with an external diameter on the order of or 51/2, the element is rotated at a speed on the order of 17 R. P. M. It is driven preferably by way of the shaft HB, as above indicated, and preferably by driving connections to the high speed motor 62.

In effecting drive of the shaft H8 from the motor 62, I preferably employ a speed-reducing mechanism and a flexible driving connection to permit freedom of tilting of the housing-like carrier H5 which supports the column |16 and the hat-supporting table |35 and related parts. Thus, and illustra-tively, I preferably provide a casing generally indicated at Iiiil (Figures 1 and 2) preferably proportioned and constructed to t in between the curved frame plates |2|3 and to rest upon the upper face of the base IG to which it is secured preferably adjustably by suitable lugs |5| and bolts or screws |52 (Figure 2). Casing |59 may be and preferably is of a built-up construction, having a base part |53 from which a sleeve-like part |54 extends vertically and upwardly to rotatably support, as by bearings |55, |56, a shaft I5? at whose upper end is mounted a pulley i513 which, by a belt |59, is in driving connection with a pulley le@ upon the lower end of the motor shaft E3. Preferably, pulley Iil is smaller than pulley itil, thus to achieve one step of speed reduction.

At the lower end of shaft |51 is a worm |62 which drives a worm wheel l |53 carried by a shaft |54 that extends horizontally and transversely of the base portion 53 of the casing which provides for it suitable bearings (not shown), thus driving shaft lfi at a further reduced speed. Shaft |54 carries a worm |5 which drives at corresponding speed reduction a worm wheel [5% secured to the lower end of a shaft itl which extends vertically.

|13, lli; in the sleeve-like portion of the casing section |63 which, like the casing section ld, is provided with suitable means for securing it to the base casing section |53.

By such an arrangement a speed reduction of from 3600 R. P. M., the illustrative speed of the motor (it, to 1'7 R. P. M., the illustrative speed for the rotary pressure and feeding element |23, is achieved. Like the belt drive between the motor 52 and the main operating shaft 22, these driving and speed reducing connections are located i in an out-of-the-way position and, moreover, will be seen to be nicely and neatly compacted in the space between the main frame plates |2`|3 and, as far as the belt il@ and pulley are concerned, underneath and within the housing-like support or bracket H5. The arrangement, furthermore, will be seen to place the axis of pivoting of the structure ||5l it, as determined by the pivot pins or studs |39, |3| (Figures l and 2) in close proximity to the line or plane of the driving belt lli?, as better appears from Figure 2; the belt llt, like the other belts, is preferably a V-shaped belt and preferably of a suitable rubber composition having a suitable degree of elasticity. Accordingly, tilting of the tiltable structure i |5| l5, etc., in clockwise direction, as viewed in Figures 1 and 2, and to the broken line position shown in Figure 1, appropriate to remove or insert the brim B relative to the tools, may thus take place without interrupting the drive and with a minimum amount of stretch of the belt |10.

The adjustability of mounting of the casing structure |50 (Figures l and 2) provide sufficient leeway for adjusting the tension of the belts |59 and Illl and in the,` preferred arrangement the axes of the motor shaft 63, casing shafts |51 and itl, and the shaft il@ of the feed and pressure element |23 are alined along the central longitudinal plane of the apparatus.

The tool structures 3|, 32 (Figures 1, 2 and 3) are preferably of identical or symmetrical construction and hence only one need be described in detail. Each tool structure is built up onto the right-hand extensions Ill and 5| (Figure 2) of the respective tool carriers 35 and 3d and, considering the details of construction of the two, reference may be had to the detailed arrangement of construction of the upper tool 3 l, better shown in Figures 4 and 6. The tool carrier extension #2| terminates in a fiat portion li |a that is in general trapezoidal in shape, being of lesser width at its outer end than near its inner end in a ratio commensurate substantially with the ratio of the inner and outer circumferences of the brim B. On its under face it has a recess lb (Figure 6) of commensurate trapezoidal shape and in the recess is secured, as by cementing, or the like, a pad of a suitable yieldable material, preferably resilient, like rubber, being of a thickness greater than the depth of the recess Il lb and having along its oblique or outwardly converging side edges Ee and lb, pad extensions lill, |82; exposed faces are inclined or beveled off to substantially merge into the under face Ble of the carrier extension lil. The front edge of the latter end of the pad 68H, being the right-hand faces or edges, as seen in Figure Ll, coincide, as indicated at l le in Figure 4, and extend at right angles to the longitudinal axis of the entire tool carrier 35.

It is against the under face of pad |30 (Figure 6) that the operative material of the tool, preferably taking the form of a suitable abrasive material in strip, sheet, or band-like form, usually in the form of so-called sandpaper, is held or supported to partake of the movement of the pad structure itself, and in Figures 2 and 6 the sandpaper in band form is indicated at |55, being of a width commensurate with the length of the pad I along the longitudinal axis of the tool carrier and with its front or right-hand edge, as viewed in Figures 2 and 4, alined o-r coinciding with the corresponding edge or face of the pad |811. The band material |85 extends preferably at right angles to the just-mentioned longitudinal axis and extends over the oblique edges lba and 58th of the pad |39 and is provided with suitable means for holding it taut and preferably with means for effecting an advancing movement thereof to move worn abrasive portions away from the under face of the pad ISS and to bring new or unused abrasive portions into operative position.

For these purposes, a preferred arrangement is as shown in Figure 6. Thus, from the right-hand oblique edge iiib of the pad m0 the band material 35 passes over an arcuate support or guide |35 whose surface is preferably cylindrical and which is preferably supported so that the axis of curvature of its surface is parallel to the oblique edge iib. Thus, the tool carrier extension 4| may have at its one end, as seen in Figure 6, a (i if extending parallel to the pad edge lllb and te which is secured a member |81 to which in turn the arcuate guide It is secured as, for

example, by providing the member |81 with longitudinal slots in its upper and lower faces and providing the sheet metal guide |36 with inwardly directed iianges respectively received in the slots of member |8`|.

Passing over member |89, the band material |35 then passes over a roller |90 suitably supported so that its axis is parallel or approximately so to the oblique pad edge |86", as by a stud shaft i9! carried at its opposite ends in iiange parts 41g and 4th of the carrier extension 4|.

Roller |59 is preferably provided with a yielding external covering, such as a rubber sleevelike part |92, and pressing against the band material |85, as the latter lays against the resilient roller ISU-|92, is a shoe |94 provided with a wear plate |95 of a material like steel and suitably mounted for movement to adjust the pressure with which the wear plate |95 presses the band material |85 against the roller ISB-|92. Such a mounting may comprise a stud shaft |95 rigidly supported at its ends in the flange parts Hg and Hh (see Figure 4) of the tool carrier extension 4|, so that the axis about which the shoe |94 may be moved is parallel to the axis of roller ISS-|92.

Suitable means are provided for adjusting the position of shoe |94 and hence for adjusting the pressure with which the band material |85 is gripped or held between the wear plate |95 and the yieldable roller ISG-|92. Such a means may comprise a thumb screw |98 (Figures 4 and 6) whose threaded shank |99 is threaded through an extension |94a (Figure 4) of the shoe |94, the free end of the threaded shank bearing against an abutment 453 (Figure 4) of the tool carrier part 4|.

Accordingly, if thumb screw |98--i 99 is turned in one direction so as to move the shoe extension |94a upwardly, as viewed in Figure 4, and away from the abutment 4U, the pressure of the shoe |94 against the roller is increased. A suitable means, such as a leaf spring 29D (Figures 4 and 6) coacting with the notched periphery of the thumb wheel |98 serves to hold the thumb scr-ew in the position in which it is set.

With such an arrangement, therefore, the resistance to movement of the band material |85 lengthwise of itself and crosswise of the face of pad |95 in a direction away from the roller and shoe structure IGS-|95, may be set or determined at will, and to hold the band material |85 taut across the face of pad and to effect, when desired, movement thereof in opposition to this resistance, I provide suitable means, such as a roller 29| (Figures 4 and 6) journaled on a stud 292 carried at one end in a bracket 209 secured to the upstanding flange-like part 4|k, and supported at its other end in the upstanding liange part 42h, the axis of roller 29| being parallel to the other oblique edge H?- of the pad |39, whence the band material |85, after passing over the roller 29|, passes between suitable means for holding and, when desired, effecting a pull upon the band material. Such a means may comprise two toothed drums 284 and 295 mounted upon shafts 295 and respectively, preferably with the axes at an angle approximating parallelism to the axis of roller 25|. The toothed drums 294, 205 mesh with each other and receive the band material |85 therebetween, in the manner better shown in Figure 6, whereby the band material may be tightly gripped and, if either or both of the drum members are rotated, a pull is exerted on the band material |85 against the resistance offered by the roller and shoe structure ISG-|95, thus to give Ithe band material an advancing movement relative to the face of pad |80.

It is desirable to adjust the spacing between the two toothed drum members 204, 255 to adjust them to diEerent thicknesses of band material or to insure adequate tightness of gripping of the band material between the meshing toothed elements of the drums, I preferably provide an adjusting arrangement so coacting with other means that also the drums may be quickly separated, as might be necessary to feed or insert the band material therebetween by hand and to permit quick restoration thereof into gripping relation, without disturbing the just-mentioned adjustment.

Such a preferred arrangement may comprise mounting the toothed drum member 264 on its shaft 258 so as to b-e driven thereby and providing a xed support for the shaft 206, as by suitable journals in the upstanding iiange parts ilk and 4th (Figures 4 and 6). Drum member 255 is, however, mounted on its shaft 297 so as -to be rotatable relative to the shaft, the latter being provided with eccentric end portions one of which is journaled in the front upstanding flange part 4|h and the other of which is journaled in the upstanding flange part 45k through which a crank-like extension thereof extends into the sleeve portion of a bracket 210 (Figures 1, 2 and 6). Bracket 2|() has a portion that overlies the upstanding flange part 4|k where it is acted upon lby a screw 2| provided with a lock nut 2|2, threaded through an arm 2|3 of a bracket 2M movably mounted upon the upstanding flange-'like part 4|k, as by a threaded stud 2|5 secured in the part Mk and provided with a thumb nut 2|6 by which the bracket 2|4 may be clamped or anchored in position relative to the part 41k.

By anchoring the bracket 2 i4, by means of the nut 2|5, so that the arm 2| 3 thereof with the screw 2li overlies the bracket 2|0, as appears better from Figures 4 and 6, the screw 2| I, slotted at its upper end so as to be operable by a tool like a screw driver, may be set relative to the now fixed arm 2|3 to move and hold the bracket 2li) in a downward position such that, through its crank-like connection with the eccentric shaft 201, the latter is so swung or rotated as to press the upper toothed drum 285 toward the lower toothed drum 254, with the band material |85 therebetween, with the desired force or pressure, so as to grip the band material |85 sufficiently to hold it taut and also to pull it, when the toothed members are rotated in appropriate direction, against the holding or gripping action of the roller and shoe structure |99-|94; the lock nut 2|2 permits locking of the screw 2|| in its adjusted position so as to insure maintenance of the desired setting.

If, however, it becomes necessary to quickly separate the toothed drum member 205 from its companion member 294, as, for example, when Stringing or threading the band material |35 through the various parts, thumb nut 2|6 is loosened up, thus permitting the bracket 2 4 to be swung about the axis of the threaded stud 2 5 so as to move the arm 2|3 with its adjusting screw 2| out of the position over the bracket 29, thus releasing the latter for manual movement upwardly and through its crank-like connection with the eccentric shaft 251 to rotate the latter throughout a suicient angle to eectseparation oi the two drum members to the desired extent. Having strung or threaded the band material through the mechanism, bracket 2|0 is manually depressed, whereupon bracket 2|4 is swung back to bring its arm 2|3 and screw 2 I I over the bracket 2|0, whence tightening up of the hand wheel or thumb nut Zit` to lock the bracket 2|4 in its restored position effects also a restoration and holding of the bracket 2|Il in its initial position and with the initially adjusted gripping pressure therebetween of the band material restored. Drum 204 has spaced peripheral grooves 2222, 234b into which extend two upstanding guides 2 |13, 2|1b of U-shaped member 2|1 to guide band 85 off of drum 254 and upwardly.

As indicated in the drawings, the band material |85 extends from roller Si) upwardly to a magazine generally indicated by the reference character 2|8 (Figures 1 and 2) where a roll of the band material is accommodated. Magazine 2 I8 is preferably of generally cylindrical construction and preferably comprises two separable parts 2| 9 and 22), of which part 2 I 9 is preferably fixedly secured in any suitable way to a bracket 22| fastened to the upper part of the upper bearing frame 24, as by bolts or screws 222.

Part 2|9, closed by the end face of bracket 22 I, and part 225, closed by its end face 223, together form a substantially completely enclosed cylindrical container or magazine, the cylindrical walls of the parts 2 I 9 and 22) being cut away to provide a slot or opening 224 through which the band material |35 emerges from the interior of the magazine and passes on downwardly to the tool carrier, specifically to the roller and shoe structure ISG-|94 (Figure 6).

As better appears in Figure 1, end part 225 of the magazine 2|8 is preferably arranged to be detachable from the part 2 I9 and the two parts are constructed to form a ready and convenient support for a roll of the band material |85. A preferred arrangement comprises a rod or shaft 225 fixed, as at 226, at the center of the disk-like end part 223 so as to form with the part 225-223 a single unit or entity. Rod 225 is of greater length than the length of the magazine 2I8 and its left-hand end (as viewed in Figure l) is of smaller diameter to be received into a hole 221 in the bracket 22I where it is releasably anchored or held, as by a pin 228, pressed inwardly as by a leaf spring 23), thus to cause the pin 228 to enter a peripheral slot in the end portion of the rod 225.

Accordingly, by withdrawing the pin 228 against the action of spring 235 sufiiciently to release the inner end of rod 225, the endmagazine part 22B with the rod 225 may be removed, a roll of band material may then be slipped onto the rod 225 and the latter with the magazine section 223 reassembled to the bracket 22| and the magazine section 2 I 9, the rod 225 thereafter functioning as an axis to support the r -i for such rotary movements as correspond to the advancing movement of the band material relative to the pad of the tool structure.

Preferably, as is better shown in Figure 2, I provide a roller over which the band material |55 moves as it is drawn out through the slot 224 of the magazine 25S. In Figure 2 the roller is indicated at 23| and it is mounted upon a stud shaft 232 whose left-hand end is `permanently fixed in the bracket 22| and whose right-hand end, when the magazine parts are assembled as above described, enters a hole 223a in the removable magazine part when the latter is assembled to the fixed magazine part, the stud shaft 232 thus insuring that the magazine part 22|! is properly alined relative to the fixed magazine part 22|, particularly with respect to the cut away portions of each (see Figure l) that form the slot or opening 224 out of which the band material |85 emerges after passing over the roller 23 I.

Though the magazine with the supply roll remains fixed, being supported by a fixed part of the frame structure, the tool structure 3| with the above-described means (see Figure 6) for holding the band material in place and for giving it an advancing movement, partakes of the movement communicated to it by the tool driving means, as above-described, the vertically extending strip of band material |85 (see Figure 2) from the magazine to the tool structure permitting these actions freely to take place.

The tool structure 32 is constructed in a similar manner though substantially inverted, the magazine for the band material, indicated by the reference character 233, being accordingly, positioned downwardly from the tool structure 32 and being similarly constructed but secured to the lower bearing frame 29 by a bracket 234 (Figure 1) in the drawings corresponding parts of the two tool structures and of the two magazines are designated by similar reference characters.

As appears better in Figures 1 and 2, and with the symmetrical or similar construction of the upper and lower tool structures 3| and 32, there are thus presented, substantially one above the other and directed toward the operating mechanism carried by the frame structure, the two driving shafts 256, 206 of the driven toothed drums 264, 284 of the two tool structures; these two shafts are connected by flexible couplings 235 and 235 to two shafts 231 and 238 that extend parallel to each otherl and one above the other (see Figures 1, 3 and 4), shaft 231 being slidably supported in suitable bearings 24| formed in the side portions of the upper bearing frame 24 and shaft 238 being rotatably supported in suitable bearings 242 formed in the lower tool carrier 34, as is indicated in Figure 1. At their ends the shafts 231Y and 233 have mounted upon them ratchet wheels 243 and 225, respectively (Figures 1 and 3).

As is better shown in Figure 3, I provide a pawl 245 to coact with the ratchet wheel 243, pawl 245 being of greater width (see Figure 1) than the width of ratchet wheel 243, since the latter partakes of a reciprocating movement axially with its shaft 231, because of the connection of the latter to the upper tool structure 23|.

Pawl 245 is pivotally mounted by a pin 246 in the forked end of a pawl carrier 241 (Figures 1 and 3) which has a round shank 228 (Figure 3) .iournaled in a bearing portion 250 of a lever arm 25| pivotally supported or fulcrumed, as at 252, by the upper bearing frame 24. Suitable means, such as a pin and washer 253, hold the pawl carrier 241 assembled to the bearing portion 250, while a leaf spring 254, anchored to the bearing portion 255 and having its free end bearing against the upper flat end face of the pawl 245 acts yieldably to resist rotary movement of the pawl carrier 241 about the axis of its journaled shank 258 and acts yieldingly to bias the pawl 255 in counter-clockwise direction and to hold it yieldingly in the positions shown in Figures 3 and 1.

The right-hand end of the pawl-carrying lever 25| (Figure 3) is in swiveled connection with a link 255 whose lower end, swiveled to the yoke 98 which is actuated when the manual member or handle 81 is actuated, as earlier above described. The effective length of link 256 is preferably adjustable or variable in any suitable way as, for example, by two nuts 257 (Figure 3) one above and the other below the pin that forms the swivel connection between lever and link 256.

Accordingly, when the manual member 87 is actuated to separate the operating tools for the removal or insertion or replacement of a hat brim therebetween, the downward or clockwise swinging of yoke S8 (Figure 3) causes, through link 256, a corresponding downward or clockwise swinging of lever 25| with the pawl 245, whence the pawl engages the ratchet wheel 243 to give it a step of rotary movement which is communicated by shaft 231 to the driven toothed drum 204 of the upper tool structure, in clockwise direction, as viewed in Figure 6, thus advancing the band material |85 by a corresponding amount relative to the face of the tool pad |80.

This action takes place during the continued actuation of the tool structure 3| and, as above indicated, is accompanied by a rapid reciprocation of ratchet wheel 243 (see Figure l) in an axial direction. The effective width, however, of the pawl 245 is suflicient to maintain engagement of the pawl with the reciprocating ratchet wheel and, depending upon the force of engagement between pawl 245 and the ratchet wheel 243, the paw] 245 can oscillate or swing about the axis of its 248 in response to the reciprocation of the ratchet wheel 243.

When the handle member 81 is restored so as to let the lower tool carrier move upwardly, thus swinging the yoke 96 (Figure 3) in counter-clockwise direction, pawl-carrying lever 25| partakes of a commensurate movement, the parts reassuming a position substantially like that in Figure 3, but ratchet wheel 243 being held against reverse rotation by a spring pawl 260.

The downward-or clockwise swing of yoke S8 (Figure 3) in response to actuation of the handle 81 to effect separation of the two tools 3|, 32 effects, as above described, a downward movement of the lower tool carrier 34 (Figures l and 2), thus carrying with it and in downward direction, the ratchet wheel 244 (Figures l and 3). Positioned in the path of downward movement of ratchet wheel 244 is an upstanding pawl 26| which is pivotally mounted by pin 262 in the forked end of a pawl carrier 263 that has a cylindrical shank 264 journaled in a bearing portion 265 formed in the bracket ||0. The pawl 26| may be constructed like a bell crank lever and hence to have an arm 26|t (Figure 3) which serves also to bias the pawl 26| in clockwise direction about its pivot 262.

Accordingly, as the lower tool carrier 34 moves downwardly and carries the ratchet wheel 244 downwardly with it, the wheel is engaged by the pawl 26| and given a step of rotary movement which is communicated through shaft 238 to the driving drum 204 of the lower tool structure 32, thus to draw and advance the abrasive band material across the upper face of the pad of the lower tool 32. This takes place during the continued actuation of the lower tool 32 which communicates to the ratchet wheel 244 a reciprocation axially; but, as better shown in Figure l, the pawl 26| is broader faced than the ratchet wheel 2'44 so that the latter cannot reciprocate out of engagement with the former. Moreover, depending upon the pressure of engagement between the ratchet wheel 244 and the pawl 26|. the reciprocation of the former may be communicated to the pawl 26| which mayroscillate about the axis of the shank 264 due to the latter being journaled in the bearing portion 265.

When the handle 8T is actuated to permit restoration in upward direction of the lower tool carrier 34, the upward movement of the latter moves the ratchet wheel 244 upward to substantially the position shown in Figure 3, but a spring pawl 266 anchored to a suitable part of the tool carrier 34 prevents reverse rotation of the pawl 244 and holds it in the position in which it had been turned by pawl 26|.

Thus, a feeding or advancing movement of the abrasive strip or band material associated with the two tool structures is dependably achieved, it being noted, referring to Figure 6, that the desired tension or tautness of each strip, as determined by the control member |98, is dependably maintained, the pull exerted by the toothed feed drums, when they are actuated in the above-described manner, being yieldingly opposed by the controllable resistance offered by the members |95|92 and by the friction of other parts relative to which the band material is drawn, such as the guiding support |86 and the pad |80. Moreover, by the above-described arrangement, it will be seen that the feeding action takes place even though the high speed actuation of the tool structures continues uninterruptedly but also, and preferably, during inactiveness of the tools upon the hat brim and thus to facilitate the advancing or feeding movement.

Preferably, and as better appears from Figure 3, a certain amount of lost motion takes place after actuation of the control lever 0l commences before the feeding or advancing movement of the band material of the two tools commences, thus to insure, in the preferred arrangement, that suflicient separation between the two tools takes place to relieve them of the load they carry or pressure they exert when operating upon the brim and so that the feeding movement takes place with the abrasive strips relieved of the burden of work; a convenient and preferred point in the train of mechanism to ini terpose this lost motion is between the pawls and their respective ratchet wheels. Thus, as shown in Figure 3, where the parts are shown positioned during operation of the tools on the brim, pawl 245 partakes of a certain amount of movement before it engages the ratchet wheel 243 and ratchet wheel 244 partakes of a certain amount of movement before it engages the pawl 26|.

Also, I provide suitable means for setting the amount or extent of feeding movement and this I prefer to achieve by varying at will the amount of the above-mentioned lost motion between the pawls and their respective ratchet wheels. Thus, by way of nut |00 and. lock nut |0| (Figure 3), I may change the position of ball member 96 and hence alter the effective length of link 95, thereby bringing the yoke 08 and hence the axis of ratchet wheel 244 nearer to or farther away from the end of pawl 26|; such an adjustment may also be effected by altering the normal position of pawl 26| relative to the axis of the pivot pin 262, as by an adjusting screw 261 (Figure 3) which is threaded in the frame part 21 and whose upper end bears against the arm 26|a of the pawl, a lock nut 268 fixing the adjustment. Thereby the upper end of the pawl 26| may be swung toward or away from the vertical plane through the axis of pawl 244, and the amount of lost motion accordingly varied.

The amount of lost motion between pawl 245 and ratchet wheel 2553 is preferably achieved by varying the eiective length of link 2'56 by which the pivoted pawl-carrying arm is connected to be moved by the yoke 93. As above indicated, this adjustment may be effected by shifting the positions of nuts 251.

Spring IB (Figure l), urging the yoke 98 upwardly about its pivot |02, causes the yoke 98 to follow faithfully the control movements of link 95, and when the yoke 963 is restored to uppermost position, the spring thus also, through the link connection 253 between the yoke 98 and the pawl-carrying arm 25|, insures restoration of the pawl 25 to uppermost position and hence prepares it for a succeeding down stroke.

Thus, having set the mechanism to effect the desired extent of feed or advancing movement for each of the abrasive strips, continuity of operation of the machine may be carried on, the apparatus, aside from the operations by the operator in effecting separation of the tool structures and replacing the hat bodies, requiring substantially no attention on the part of the operator except to renew the supply of abrasive band material in the manner above described, it being noted that the magazines Zit and 233 (Figures i and 2) are constructed to eiiect speedy and quick recharging with new rolls of abrasive band material.

Details of the operation of the mechanism will be clear in View of what is set forth above; it might be noted, however, that the work on the part of the operator is simple and foolproof. Thus, the motor 62 having been started and putting the various mechanisms above described into operation and with the two tool structures set into motion, preferably at the high speeds abovementioned, and the hat-feeding or rotating member |22|23 thus set into motion at relatively low speed, the operator, having actuated the lever 81 which is conveniently positioned to be operated by the left-hand to separate the two tool structures, simply leaves the lever 81 and the parts controlled by it in their locked position due to the toggle action between links 93 and 95 (Figure 1), and is free to place a hat body over the rotary member |22|23 with the greater portion of its brim resting upon the top face |a of the support |35 (Figures 1 and 2), the latter parts being manually swung into the dotted line position shown in Figure 1. Swinging the latter structure back toward and Vinto its full line position, the brim B is entered between the separated tool structures 3|, 32, while the yielding rotary member |23 presses the lower side portion of the crown C against the curved face of the member |44 (Figures 1, 2 and 4), the coaction between members |23 and |44 insuring that the brim is positioned completely within the range of action of the two tool structures, particularly the upper one, and eiecting also a slow rotary movement of the hat body to traverse the brim at the desired speed but steadily and uniformly relative to the two tool structures whose operative surfaces are at once made eiective upon the hat brim when the operator restores the lever 8l to bring the lower tool structure 32 in an upward direction and to permit the spring 83 to come into action to eiTect the desired pressure of operation of the two tools upon the brim that is interposed between them.

As the tools operate a steady and uniform progression of the brim B relative to the two tools proceeds. thus insuring that the cutting or abrading action of the two tools, above described, is uniformly eiected throughout the entire extent of the brim not only circumferentially but also radially, the rotary member |23 insuring not only a steady feeding or rotating action on the hat body but also that the entire radial extent of the upper face of that portion of the brim B that is between the two tools is always exposed to the upper tool beyond the thin and almost knife-like edge of member |124 in the region of point y of Figure 4; this latter action is effective to insure that the entire radial extent of that portion of the hat brim that is at any moment between the tools is also presented to the lower tool 32.

Rotary hat-feeding member IEE-|23 may bel urged toward the curved face of member |44 by any suitable means. Preferably, the tension of belt Il@ (Figures l and 2) is utilized to eiect this action, it being noted that, upon swinging the hat-supporting structure |35| i5 in clockwise position of Figure l, the structure has its center of gravity shifted sufficiently to the right so as to overcome the tension of the belt |10 and hence so that the structure remains in such position while the operator replaces the hat body. Preferably, suitable means are provided to limit movement in clockwise direction, as by the engagement of the side walls of Jthe housing-like part H5 with the hinge brackets |2, |21, as indicated in Figure l.

The operator, of course, swings the hat-carrying structure in clockwise direction after having actuated the control lever 8l to separate the tool structures and it will be noted that the manual control of the hat-carrying structure is easy and simple. In swinging it away from the tools, the movement is aided by the increasing leverage through which the weight of the parts acts as the center of gravity is shifted toward the right, as viewed in Figure l, while in restoring the hat-carrying structure, the tension of the belt Is assists in such movement.

Thus, it will be seen that the manual manipulations on the part of the operator are simple and may be carried on with rapidity and ease and more particularly with reliability as to precision of association of the brim with the operating tools.

The entire apparatus excepting for the two tool structures, the two magazines, the operating lever, and the hat-carrying structure, is preferably totally enclosed to protect it against foreign material, particularly particles of bers cut off or abraded from the brim by the operating tools and also to protect the personnel working with or around the apparatus. A preferred form of enclosure comprises two casing sections 2l! and N2 of suitable sheet-like material, preferably in the ferm of aluminum castings. The two casing sections are substantially identical in shape and together give the appearance of a frustrum of a cone whose lower peripheral portions .rlt into a peripheral bezel 2'53 provided at the upper end of the base I@ (Figures l and 2), the truste-conical side portions of the casing merging at their upper ends into substantially a hemisphere but at the rear of the machine, that is, at the left, as seen in Figures 1, 2 and (i, the two casing sections 21|, 212 bulging outwardly to accommodate or enclose certain of the parts that project in that direction to a great-er distance yirection, to, for example, the dotted liney than others. As appears clearly from Figures 1 4, the two casing sections are broken or cut away from their mating edges at the front (toward the right in Figures l, 2 and 4) to form suitable apertures through which the housinglike support I i5 projects near the lower end and also, in the upper regions, through whichl the operating lever S1 and its shaft 88, the brackets for the upper and lower magazines, and the tool carrier extensions 4| and 5|, together with the feed drive shafts 231 and 238, project.

Thus, there remains exposed normally such parts as need be accessible for normal operation, such as the tool structures, the hat-supporting and feeding structure, the operating lever, the magazines for the abrasive material, and the controls for tensioning the abrasive band material and for threading it through the tool structures.

Preferably, the enclosure, preferably made up of the two casing sections 21| and 212, is arranged to be readily detachable to gain access to the mechanism or parts enclosed thereby, and in the preferred arrangement, with the lower substantially semi-circular edge portions of the sections 21|, 212 tted into the base IB, as above-described, I provide suitable means operative preferably at the upper ends of the sections to hold them together and to attach them to the builtup frame of the apparatus.

Thus, at their upper midpoints the two casing sections (Figure 3) are provided with lugs 215 anl 21B to which, as by brackets 211 and 218, respectively, are secured upstanding pins or studs 219 and 280 which, as better appears from Figure 5, are positioned preferably substantially diametrically opposed to each other relative to the circular cross-section of the assembled casing sections 21|, 212.

Lugs 215 and 216 may be formed as part of internal flanges 21|a and 212a formed integrally with or secured to the casing sections 21| and 212, respectively, flanges 21|a and 212e, when the casing sections are assembled, forming an inwardly directed circular flange whose inner circular edge face takes against the circular periphery 282iL oi a disk-like frame element 282 (Figures 2, 3 and 5) which is secured to be concentric or coaxial with the circular bezel 213 in the base l) and with which the lower edge portions of the casing sections intert (Figures 1 and 2). This frame element 282 is secured to the upper end of the upper bearing frame 24 (Figures 1, 2 and 3), as by screws 233, being provided with an eccentric aperture 282i) which fits about the upper end bearing structure 23, as appears better in Figure 2.

By means of pins or studs 285 and 265, there are pivoted to the plate member 282 (Figures 3 and 5) levers 281 and 28B, respectively, provided at their outer ends with hook portions 281 and 288e for engagement, respectively, with' the pins 219 and 2S() carried by the casing sections 21|, 212, thus to hold the latter against separation from each other and from their above-mentioned concentric supports.

These levers are preferably spring biased, as by springs 283 and 29?, in a direction to hold them hooked about the pins, as shown in Figure 5, and the inner ends of the two levers preferably overlie one another and are engaged by a collar or other enlargement 293 carried by the inner end of a plunger 294 slidably mounted in a bracket 295 secured to the frame part 232. Plunger 254 has at its cuter end a head 235 between which and the bracket 295 is a spring 291 that biases the plunger in a direction to hold the enlargement 293 against one face of the bracket 295 and thus also to position the head 295 closely adjacent an aperture 223 in the enclosing casing and formed by two appropriate cutouts in the two casing sections 21|, 212.

Accordingly, when it is desired to release the casing sections from the frame, the plunger 29E is pressed inwardly by actuating the head 296 through the aperture 29S against the action of spring 291, thus forcing the inner ends of levers 281 and 28B in directions to move their' hooked ends out of engagement with the pins 219 and 28D, whence the casing sections may be removed, Assembly of the casing sections to the frame structure is accomplished by a reverse sequence of operations.

Thus, it will be seen that there has been provided in this invention an apparatus in which the various objects hereinabove noted, together with many thoroughly practical advantages, are successfully achieved. The apparatus is well adapted for such high speeds of actuation of its operating tools as pointed out above, is of durable and safe construction to function at such high speeds, and is of highly effective and emcient operation and action. Moreover, it is well adapted to meet the varying conditions of hard practical use.

As many possible embodiments may be made of the mechanical features of the above invention and as the art herein described might be varied in various parts, all without departing from the scope of the invention, it is to be understood that all matter hereinabove set forth, or shown in the accompanying drawings is to be interpreted as illustrative and not in a limiting sense.

I claim:

1. In apparatus of the class described, in combination, a frame structure having a base portion and spaced upstanding side portions between which is mounted a driving motor and having an upper frame portion, two tools for operating upon the respective sides of the brim of a hat, mechanism supported by said upper frame portion for actuating both of said two tools and for permitting movement of separation therebetween to permit insertion or removal of the brim of a hat, means for holding a hat body and for giving it a rotary movement to progress the brim relative to said two tools and comprising an external member having means mounting it from said frame structure and in a position adjacent said two tools to limit the extent of insertion of the brim between said two tools by engagement with said member of part of the outside face of the side portion of the crown of the hat and a rotary member of lesser axial height and lesser radius than those of the hat crown engaging tangentially the inside face of the part of the side portion of the crown engaged by said first-mentioned member with means causing said rotary member to press the part of the side portion of the crown engaged by it against said firstmentioned member to maintain rolling driving contact with the inside face of the side portion of the crown and to force successive portions of the brim inwardly between said two tools to the extent permitted by said first-mentioned member, means forming driving connections between said motor and said mechanism to actuate said tools at suitable operating speed and means forming driving connections between said motor and said rotary member to drive the latter at a relatively low peripheral speed to effect progression of the brim between said two tools at the desired rate.

2. An apparatus as claimed in claim 1 in which said tool-actuating mechanism comprises a substantially vertically extending shaft means, said driving motor having a shaft in substantial alinement with said shaft means, the driving connections between said mechanism and said motor being between said shaft means and said motor shaft and adapted to counteract transmission of vibrations from one to the other.

3. An apparatus as claimed in claim l in which said tool-actuating mechanism comprises a substantially vertically extending shaft means, said driving motor having a shaft in substantial alinement with said shaft means, the driving connections between said mechanism and said motor comprising pulley means on said shaft means and upon said motor shaft, a jack shaft having pulley means, and belt means for said pulley means.

4. An apparatus as claimed in claim 1 in which there are provided means comprising an auxiliary frame for rotatably supporting said rotary member and means supporting said auxiliary frame for movement relative to said frame structure in directions to move said rotary member toward or away from said external member` to respectively start or halt rotary movement of the hat body according as the engaged portion of the hat body is pressed against said external member upon movement of said rotary member toward the latter or is released from being pressed thereagainst upon movement of said rotary member away from said external member, and to permit insertion or removal of the portion of the hat relative to said coacting rotary member and external member when it is desired to effect insertion or removal of a hat brim relative to said tools.

5. An apparatus as claimed in claim 1 in which there are provided means mounting said rotary member for movement in a direction toward or away from said external member and the driving connections between said driving motor and said rotary member include a generally vertically extending driven shaft having at its upper end driving connection with said rotary member and having adjacent its lower end flexible driving connections with said motor to maintain drive of said shaft and rotary member during movement of the latter toward or away from said external member.

6. An apparatus as claimed in claim 1 in which a driving shaft extends downwardly from said rotary member, auxiliary frame means supporting said driving shaft for rotation and having means supporting it from said frame structure to pivot about an axis adjacent the lower end of the latter, said driving connections between said rotary member and said driving motor comprising said driving shaft, and flexible means connected to the lower end of said driving shaft to maintain driving connection during movement of said auxiliary frame about its axis of pivoting.

'7. An apparatus as claimed in claim l in which a driving shaft extends downwardly from said rotary member, auxiliary frame means supporting said driving shaft for rotation and having means supporting it from said frame structure to pivot about an axis adjacent the lower end of the latter, the driving connections between said rotary member and said driving motor comprising belt and pulley means, one of which lpulley means is on the lower end of said driving shaft, said belt and pulley means being so related to the axis of pivoting of said auxiliary frame that pivoting movement of the latter may take place without disrupting the drive of said belt and pulley means.

8. An apparatus as claimed in claim 1 in which there is provided means including a manually operable member for effecting movement of separation between said two tools, and means mounting said rotary member moveable relative to said external member and throughout a range of movement toward or away from said tools on the order of the radial dimension of the brim, and means for controlling movement of said rotary member, whereby, upon said rotary member being moved away from said external member, the space between the two is adequate to accommodate the radial dimension of the brim as the hat body is inserted or removed relative to the two tools.

9. An apparatus as claimed in claim 1 in which there is provided means including a manually operable member for effecting separating movement between said two tools, said means having means for locking the movable tool in separated position, and means for effecting movement of approach or of separation between said rotary member and its coacting external member to respectively start or stop rotary movement of the hat body and upon movement of separation to permit removal of a hat body therefrom and of the hat brim from in between the separated tools.

10. ,An apparatus as claimed in claim 1 in which there is provided means including linkages that form a toggle and a manually operable member for actuating said means to effect movement of separation between said two tools, said toggleforming linkages assuming self-locking positions upon completion of said separating movement.

11.v In apparatus of the class described, in combination, two juxtaposed tool means having means movably mounting one of them for movement toward or away from the other to permit the insertion or removal of a portion of a hat body like the brim, said tool means each comprising operating material in band-like form and means for supporting said material with means adapted upon actuation to feed sai-d band-like material relative to said supporting means, driver means for each of said feeding means, the driver means for the feeding means of said movable tool having means mounting it to partake of movement with said tool, movable means for effecting movement of said movable tool and of said movable driver means, means responsive to movement of said movably mounted driver means operating to drive it, and means responsive to movement of said movable means operating to drive the other driver means.

12. An apparatus as claimed in claim 11 in which one of said driver means comprises a ratchet wheel and its driving means comprises a pawl.

13. An apparatus as claimed in claim 11 in which at least one of said driving means includes means having a lost motion connection.

14. An apparatus as claimed in claim 1l in which both of said driver means comprise ratchet wheels, the driving means for the ratchet wheel movable with the movable tool comprising pawl means relatively fixed, thereby to eiect rotary movement of the ratchet wheel, and the driving means for the other ratchet wheel comprising pawl means and means causing it to move in response to movement of said movable means/fi 15. In apparatus of the class described, in combination, a tool for operating upona'hat and having an eective operating portion/in the form of strip material with means adapted upon actuation to give the latter an advancing movement, means for supporting and actuating said tool to give it a movement relative to the hat body operated upon that comprises motion of reciprocation, a ratchet wheel for driving said strip-advancing means and connected to partake of reciprocation with said tool, a movable member relative to which said ratchet wheel reciprocates, and -pawl means carried by said movable member and actuatable thereby to operate said ratchet wheel and eiective upon the latter throughout the range of reciprocation thereof.

16. In apparatus of the class described, in combination, a tool for operating upon a hat and having an eiective operating portion in the form of strip material with means adapted upon actuation to give the latter an advancing movement, means for supporting and actuating said tool to give it a movement relative to the hat body operated upon that comprises motion of reciprocation, a ratchet Wheel for driving said strip-advancing means and connected to partake of reciprocation with said tool, a movable member relative t which said ratchet wheel reciprocates, pawl means for coaction with said ratchet means, and means movably mounting said pawl means on said movable member to partake of movement in response to the reciprocating movement of said ratchet wheel.

17. In apparatus of the class described, in combination, a tool for operating upon a hat and having an effective operating portion in the form of strip material with means adapted upon actuation to give the latter an advancing movement, means for supporting and actuating said tool to give it a movement relative to the hat body operated upon that comprises motion of reciprocation, a ratchet wheel for driving said strip-advancing means and connected to partake of reciprocation with said tool, said tool-mounting and driving means comprising also means adapted upon actuation to effect movement of said tool and of said ratchet wheel in the direction of the plane of the ratchet wheel, pawl means, and means mounting said pawl to hold it against movement upon movement of said ratchet wheel in the direction of its plane, thereby to effect rotary movement of said ratchet Wheel.

18. An apparatus as claimed in claim 17 in which the mounting means for said pawl includes movable connections permitting the pawl to partake of recprocation in response to the motion of reciprocation of the ratchet wheel.

19. In apparatus of the class described, in com- I bination, a frame having tool means for operating upon the brim of a hat, a hat support having substantially flat means upon which at least a portion of the hat brim may rest, a member adjacent said tool means and positioned to be engaged by the side portion of the crown of the hat and thereby to substantially x the `position of the brim portion operated upon by said tool means relative to the latter, and driven rotary means of lesser axial height and of lesser radius than the interior of the crown of the hat, said driven rotary means having means mounting it relative to said hat support in a position to extend freely into the hat crown and tangentially engage in rolling contact a portion of the inside face of the side portion of the crown in juxtaposition to said member for effecting a rotary movement of the hat and movement of progression of the brim relative to said tool means.

20. In apparatus of the class described, in combination, a frame having tool means for operating upon the upper face of the brim of a hat, a hat support having means upon which at least a portion of the hat brim may rest, a member adjacent said tool means and positioned to be engaged by the side portion of the crown of the hat and thereby to substantially x the position of the brim portion operated upon by said tool means relative to the latter, and driven rotary means of lesser axial height and of lesser radius than the interior of the crown of the hat, said driven rotary means having means mounting it relative to said hat support in a position to extend freely into the hat crown and tangentially engage in rolling Contact a portion of the inside face of the side portion of the crown in juxtaposition to said member for effecting a rotary movement of the hat and movement of progression of the brim relative to said tool means, said member having a face in the direction toward said tool means shaped to permit the latter to operate up to the junction of the crown with the brim and having that face thereof that engages the side of the crown curved in the direction of curvature of the crown side.

21. In apparatus of the class described in which there is frame means having a hat-operating tool that has an operating means in strip form with means for supporting and feeding the operating means relative to the tool means and means for giving said tool means motion relative to the hat body operated upon, the combination of a magazine for the strip form of operating means comprising a magazine casing of at least two separable parts, means mounting one of the parts on the frame means, means detachably securing the other part thereto, said magazine casing having an opening through which the operating means in strip form passes t0 said tool means, said means for detachably securing the separable casing part 4comprising a shaft-like stud secured to the latter and functioning to support a roll of the operating means in strip form, said magazine casing having a stud-like member adjacent its opening to guide withdrawn strip form of operating means therethrough, said stud-like member being secured at one end thereof to said frame means, said separable casing part and the other end of said stud-like member having portions that interfit upon assembly of said separable casing part to the other.

22. In apparatus of the class described, in combination, two members supporting respectively two tools for operating upon the opposed faces of the -brim of a hat, and means for electing separation thereof to permit insertion or removal of a hat brim and comprising toggle means the links of which have a range of operation to assume such alinement as eiects locking, and means for actuating said toggle means.

23. In apparatus of the class described, in combination, two members supporting respectively two tools for operating upon the opposed faces of the brim of a hatl driving means for said two members to aotuate said two tools relative to the hat brim, said driving means comprising two eccentric means having operative connections respectively with said two members, one of said operative connections comprising sleeve-like means on one of said members slidable axially relative to its eccentric means whereby said member is movable axially in directions to effect separation or approach between said two tool means, and means for controlling axial movement 0f said member. f

24. An apparatus as claimed in claim 23` in which the eccentric means relative to which the sleeve means is axially movable comprises a cylinrical support for said sleeve means, a `driven eccentric, and bearing means between said eccentric and said cylindrical support, whereby said bearing means permits relative rotary movement; between said eccentric and said support and the movement between said sleeve means and said support is primarily a sliding movement.

25. In apparatus of the class described, in combination, a pair of tool carriers each having at one end thereof an abrasive tool, said yabrasive tools facing each other and adapted to receive therebetween a portion of the brim of a hat, means mounting and actuating said tool carriers to give their tools operating motions and to give the tool operating upon the upper side of the brim a motion such that any operating point on the tool moves in a curved closed path, whereby said upper brim tool has a component of movement toward and away from the side of the crown of the hat, a relatively fixed means positioned adjacent said upper brim tool and substantially at the end of its movement in the clirection toward the crown of the hat and to thereby prevent the tool from engaging the side of the hat crown, and means engaging the inside of that `portion of the side of the hat crown that is engaged by said relatively xed means for urging the crown side against said relatively fixed means and thereby to insure that the inner radial portions of the upper side of the brim are within the scope of the aforesaid motion of said upper brim tool, said relatively xed means having a `cross-section that is tapered in a direction toward the apex of the angle between the brim and the crown side to thereby interpose a minimum, if any, thickness between the upper brim tool when at its outermost position and the crown side.

26. In apparatus of the class described, in combination, a pair of tool carriers each having at one end thereof an abrasive tool, said abrasive tools facing each other and adapted to receive therebetween a portion of the brim of a hat, means mounting and driving said two tool carriers to give the two tools operating motions relative to the hat brim received therebetween, said means comprising shaft means having two eccentric means, means in the form of a rotary bearing forming a connection between one of said eccentric means and one of said tool carriers, means forming a combined rotary and axiallyshiftable connection between the other of said eccentric means and the other of said tool carriers comprising a sleeve-like member mounted rotatably relative to said other eccentric means and a sleeve-like part on the other of said tool carriers substantially telescopically fitted over said sleeve-like member and axially shiftable relative thereto, whereby said other tool carrier may be shifted axially of its eccentric means to change the spacing between the two tools, and means for controlling the shifting axially of said other tool i carrier.

27. In apparatus of the class described, in combination, a pair of tool carriers each having at one end thereof an abrasive tool, said abrasive tools facing each other and adapted to receive therebetween a portion of the brim of a hat, means mounting and driving said two tool carriers to give the two tools operating motions relative to the hat brim received therebetween, said means comprising shaft means having two eccentric means, means in the form of a rotary .bearing forming a connection between one of said eccentric means and one of said tool carriers, means forming a combined rotary and axially-shiftable connection between the other of said eccentric means and the other of said tool carriers whereby said other tool carrier may be shifted axially of its eccentric means to change the spacing between the two tools, means for controlling the shifting axially of said other tool carrier, means for urging said axially shiftable tool carrier axially toward the other and thereby lessen the distance between said two tools, said controlling means comprising a member movable in the direction of axial shift of said other tool carrier, the latter and said movable mem-ber having coacting bearing portions whereby the operating motion of said other tool carrier may freely take place relative to said movable mem-ber, and means for actuating said movable member.

28. In apparatus of the class described, in combination, a pair of tool carriers each having at one end thereof an abrasive tool, said abrasive tools facing each other and adapted to receive therebetween a portion of the brim of a hat, means mounting and driving said two tool carriers to give the two tools operating motions relative to the hat brim received therebetween, said means comprising shaft means having two eccentric means, means in the form of a rotary bearing forming a connection between one of said eccentric means and one of said tool carriers, means forming a combined rotary and axiallyshiftable connection between the other of said eccentric means and the other of said tool carriers whereby said other tool carrier may be shifted axially of its eccentric means to change the spacing between the two tools, means for controlling the shifting axially of said other tool carrier, said axially shiftable tool carrier having two ,portions one on each side of its axis, said shift-controlling means comprising a movable yoke-like member whose two portions are respectively juxtaposed to said two carrier portions, and means for controlling movement of said yoke-like member.

29. In apparatus of the class described, in combination, a pair of tool carriers each having at one end thereof an abrasive tool, said abrasive tools facing each other and adapted to receive therebetween a portion of the brim of a hat, means mounting and actuating said tool carriers to give their tools operating motions and to permit movement of one carrier toward the other thereby to vary the spacing between said tools, spring means urging said movable tool carrier in a direction to lessen the distance between said two tools and means for controlling the separation between said two tools and for limiting their approaching movement comprising controllable movable means, said movable means and said movable tool carrier having coacting portions through which when said movable means is moved in one direction said movable tool carrier is moved in a direction to separate said tools against the action of said spring means, and means limiting movement of said movable means in reverse direction to form a stop to prevent saidspring means from moving said movable carrier suiiciently to cause its tool to contact the tool of the other carrier.

30. In apparatus of the class described, in combination, a frame structure comprising a base portion supporting an upstanding frame portion,

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