Roughing machine having tool position adjusting mechanism

A roughing machine for roughing the margin of an upper of a shoe assembly comprised of a last having an insole on its bottom and the upper mounted thereon with the upper margin lying against and being secured to the insole periphery. The machine is so constructed as to enable a roughing tool to engage the upper margin a relatively great or a relatively small distance inwardly of the periphery of the shoe assembly bottom during movement of the upper margin past the roughing tool and the machine incorporates an automatically operable mechanism for placing the roughing tool in one or the other of these positions.

BACKGROUND OF THE INVENTION 
Each of U.S. Pat. Nos. 3,077,098, 3,298,048 and 3,843,985 discloses a 
roughing machine capable of roughing the margin of an upper of a shoe 
assembly comprised of a last having an insole located on its bottom and 
the upper mounted thereon with the upper margin lying against and being 
secured to the insole periphery. These machines are so constructed as to 
enable a roughing tool to engage the upper margin a relatively great or a 
relatively small distance inwardly of the periphery of the shoe assembly 
bottom during movement of the upper margin past the roughing tool. 
In the machine of U.S. Pat. No 3,077,098 the roughing tool is caused to be 
displaced from a relatively great distance inwardly of the periphery of 
the shoe assembly bottom to a relatively small distance inwardly of the 
periphery of the shoe assembly bottom in response to the approach of the 
widest part of the shoe assembly bottom, which is at the ball break, to 
the roughing tool so that the roughing tool roughs the upper margin at the 
relatively small distance inwardly of the shoe assembly bottom at the ball 
breaks and in the shank and forepart portions that are on opposite sides 
of the ball breaks. 
In the machine of U.S. Pat. No. 3,298,048 the position of the roughing tool 
with respect to the periphery of the shoe assembly bottom is adjusted by 
manually operating a foot pedal. 
In the machine of U.S. Pat. No. 3,843,985, the roughing tool is caused to 
be displaced from a relatively great distance inwardly of the periphery of 
the shoe assembly bottom to a relatively small distance inwardly of the 
periphery of the shoe assembly bottom during rotary motion of the toe 
portion of the upper margin past the roughing tool. 
SUMMARY OF THE INVENTION 
It has been found to be desirable to displace the roughing tool from a 
relatively great distance inwardly of the periphery of the shoe assembly 
bottom to a relatively small distance inwardly of the periphery of the 
shoe assembly bottom during the movement past the roughing tool of the 
portion of the upper margin that extends between the regions of the ball 
breaks and the toe end extremity of the upper margin. This invention 
provides a machine that automatically performs this displacement between 
the regions of the ball breaks and the toe end extremity of the upper 
margin or between any other desired portions of the upper margin. 
As with the machine of U.S. Pat. No. 3,843,985, the machine of this 
invention incorporates a housing, a roughing tool mounted to the housing 
for forward-rearward movement, drive means for moving the roughing tool 
between forward and rearward positions with respect to the housing, a 
table, a slide mounted to the table for movement with respect to the 
table, a shoe assembly support mounted to the slide for supporting a shoe 
assmebly bottom-up, shoe assembly support moving means that includes means 
for moving the slide with respect to the table to thereby move portions of 
the upper margin past the roughing tool, and operating means effective 
during the movement of the upper margin portions past the roughing tool to 
cause such movements of the housing as to enable the roughing tool to 
engage the upper margin a relatively great distance inwardly of the 
periphery of the shoe assembly bottom when the roughing tool is in said 
forward position and to enable the roughing tool to engage the upper 
margin a relatively small distance inwardly of the periphery of the shoe 
assembly bottom when the roughing tool is in said rearward position. 
The machine of U.S. Pat. No. 3,843,985 has been modified, in accordance 
with this invention, by providing a control member mounted to the table 
and an actuator member mounted to the slide. These members are so 
constructed and arranged as to be in intersecting relationship or 
non-intersecting relationship during the operation of the shoe assembly 
support moving means. Adjusting means are incorporated in the machine that 
so connect the members to the drive means as to cause the drive means to 
place the roughing tool in one of its positions when the members are in 
non-intersecting relationship and to place the roughing tool in the other 
of its positions when the members are in intersecting relationship.

DESCRIPTION OF THE PREFERRED EMBODIMENT 
The operator is intended to stand in front of the machine as seen in FIG. 
1, to the left of the machine as seen in FIG. 2 and to the right of the 
machine as seen in FIG. 3. Directions extending toward the operator will 
be designated as "forward" and directions extending away from the operator 
will be designated as "rearward" . The front of the machine is closest to 
the operator and the back of the machine is furthermost from the operator. 
The machine, as shown in FIGS. 1-3, includes a shoe assembly mount section 
10 and a tool section 12 located rearwardly of the section 10. 
Referring to FIG. 4, the section 10 includes a stationary base 14 having a 
stationary sleeve 16 upstanding therefrom. A turnable 18 is mounted to the 
base 14 and the sleeve 16 for rotation in a horizontal plane. As shown in 
FIGS. 7-10, a slide 20 is slidably guided in the turntable 18 for 
recipocating motion in a horizontal plane by means of bushing 22 on the 
slide 20 that are slidable on rods 24 that are affixed to and extend 
across the top of the turntable 18. 
Referring to FIGS. 7-10, a post 26 is rigidly mounted to the slide 20 and a 
last pin 28, that acts as a shoe assembly supporting element, extends 
upwardly of the post 26. An air operated motor 30 is rigidly mounted to 
the the post 26. The piston rod 32 of the motor 30 is secured to one end 
of a bracket 34 and a bolt 36 is rotatably mounted to the other end of the 
bracket 34. The bolt 36 is threaded into a stand 38 and a knob 40 is 
affixed to the end of the bolt 36 that is remote from the bracket 34. The 
stand 38 is slidably guided, by means of gibs 42, in the slide 20 for 
reciprocating motion in directions that are parallel to the directions of 
reciprocating motion of the slide 20 in the turntable 18. 
The stand 38 incorporates an air operated motor 44 that includes a cylinder 
46 and an upwardly extending and vertically movable piston rod 48. A toe 
pad 50, that acts as a shoe assembly supporting element, is affixed to the 
top of the piston rod 48. The stand 38 also incorporates an air actuated 
motor 52 that includes a cylinder 54 in the stand and a downwardly 
extending vertically moveable piston rod 55. A brake pad 56 is affixed to 
the bottom of the piston rod 55 and is in registry with a flat surface 58 
of the slide 20. 
Another air operated motor 60, mounted to the stand 38, has a piston rod 62 
extending upwardly thereof. A clevis 64, at the top of the piston rod 62, 
pivotally mounts a toe stop 66 for swinging movement about the axis of a 
pin 68. The toe stop 66 is located adjacent to the toe pad 50 and on the 
opposite side of the toe pad 50 from the last pin 28. A ledge 70 is 
mounted to the clevis 64 and a compression spring 72 interposed between 
the ledge 70 and a lug 74 affixed to the toe stop 66 yieldably urges the 
toe stop 66 counterclockwise (FIG. 7) about the axis of the pin 68. A 
valve 76, mounted to the ledge 70, is in registry with a cam surface 78 on 
the lug 74, the spring 72 normally yieldably urging the cam surface 78 
upwardly and away from the spool of the valve 76. 
A bracket 80 is so rotatably mounted to an unthreaded portion of the bolt 
36 adjacent to the knob 40 that the bracket is not moveable along the 
longitudinal axis of the bolt. The bracket 80 is slidably mounted in the 
slide 20 by means of flanges 82 slidable in the gibs 42. A plate 84 is 
fixed to the bracket 80 and extends horizontally from the bracket 80 
towards the post 26 over the slide 20. A bracket 86 is fixed to the gibs 
42 of the slide 20 in such a manner as to straddle the piston rod 32. A 
link 88 is pivoted to a post 90 that is upstanding from the bracket 86. 
The link 88 is pivoted by a pin 92 to a link 94. The link 94 is pivoted 
intermediate its ends by a pin 96 to a flange 98 of the plate 84. 
A beam 100 is located beneath the plate 84 and is slidably mounted to the 
plate 84 for movement lengthwise of the slide 20 by means of a pair of 
bolts 102 that are threaded into the beam 100 and extend upwardly thereof 
through a longitudinal slot 104 in the plate 84. The bolts 102 are movable 
in the slot 104 and washers 106 interposed between the heads of the bolts 
102 and the top of the plate 84 retain the beam 100 against the bottom of 
the plate 84. A pin 108 extending upwardly of the beam 100 through the 
slot 104 is slidably received in a slot 110 in the end of the link 94 
remote from the pin 92 and on the opposite side of the pin 96 as the pin 
92. 
A pair of posts 112 are rigidly secured to a rod 114 that is so mounted to 
the turntable 18 as to extend lengthwise of the slide 20. A bolt 116 
extends between and is rotatably mounted in the posts 112 and a bar 118 is 
fixedly mounted to the posts 112 so as to extend alongside the bolt 116. A 
valve mount 120 is threaded onto the bolt 116 and is slidably mounted in 
the bar 118 whereby rotation of the bolt 116 by a knob 121 can effect 
movement of the valve mount 120 lengthwise of the bolt 116 towards and 
away from the beam 100. A valve 122 is so mounted to the valve mount 120 
as to be in registration with a valve actuating cam 123 that is mounted to 
the end of the beam 100 that is remote from the bracket 80. 
A rack 124 (FIGS. 4 and 9), mounted to the bottom of the slide 20, is in 
mesh with a gear 126. The gear 126 is fixed to a shaft 128 (FIG. 4) that 
depends from and is rotatable in the sleeve 16. The turntable 18 is 
rotable about the vertical axis of the sleeve 16. A gear 180 is secured to 
the shaft 128 below the base 14 and, below the gear 130, the shaft 128 is 
affixed to an upper element of a pneumatically operated clutch 132 and 
extends through the lower element of this clutch. 
A gear 134, secured to the turntable 18, is in mesh with a gear 136 that is 
rigidly secured to a shaft 138. The shaft 138, which is rotatably mounted 
in and extends below the base 14, is affixed to an upper element of a 
pneumatically operated clutch 140 and extends through the lower element of 
the clutch 140. 
The gear 130 is in mesh with a gear 142 that is rigidly mounted to a shaft 
144. The shaft 144 is rotatably mounted in and extends below the base 14 
and is affixed to an upper element of a pneumatically operated clutch 146. 
A plate 148 is located below the base 14 and is secured to the base 14 by 
columns 150. A drive shaft 152, connected by a gear 154 to a source of 
power (not shown), is rotatably mounted in the plate 148 and is connected 
to the lower element of the clutch 146. The bottoms of the shafts 128 and 
138 are also rotatably mounted in the plate 148. A sprocket 156 secured to 
the shaft 152 is drivingly connected by a chain 158 to a sprocket 160. The 
sprocket 160 is rotatably mounted to the shaft 128 and is secured to the 
lower element of the clutch 132. A sprocket 162 secured to the shaft 152 
is drivingly connected by a chain 164 to a sprocket 166. The sprocket 166 
is rotatably mounted to the shaft 138 and is secured to the lower element 
of the clutch 140. 
Referring to FIGS. 4, 6 and 9, a shaft 168 extends through and is rotatably 
mounted in the shaft 128 and the clutch 132. An arm 170 is secured to the 
top of the shaft 168 and is located above the tops of the rack 124 and the 
gear 126. A cam 172 is secured to the bottom of the shaft 168 and is 
located below the plate 148. A tension spring 174, connected to and 
extending between the cam 172 and a clip 176 secured to the plate 148, 
yieldably urges the cam 172, together with the shaft 168 and the arm 170, 
about the axis of the shaft 168 to a position wherein the cam 172 abuts a 
pin 178 that is secured to and depends from the plate 148. A valve 180 is 
mounted to the plate 148 and is so located as to be actuated by the cam 
172 when the cam 172 is moving about the axis of the shaft 168 and away 
from its position of abutment with the pin 178. A pair of cams 182 and 184 
having radially projecting cam lobes 186 and 188 are mounted to the bottom 
of the shaft 138 below the plate 148. The cam lobe 186 is in intersecting 
relationship, during rotation of the shaft 138, with a valve 190 and the 
cam lobe 188 is in intersecting relationship, during rotation of the shaft 
138, with a valve 192. The valves 190 and 192 are mounted to the plate 
148. 
Referring to FIGS. 6-8, a finger 194 is mounted to the end of the slide 20 
remote from the stand 38 and a finger 196 is mounted to the stand 38. The 
fingers 194 and 196 are located on opposite sides of the shaft 138 and are 
in intersecting relationship with the arm 170 during movement of the slide 
20 with respect to the turntable 18 in the manner described below. 
As shown in FIG. 8, a projection 198 mounted to the stand 38 is in 
intersecting relationship with a lug 200 that is mounted to the rod 114 
and the lowermost end of the bracket 86, as seen in FIG. 8, is in 
intersecting relationship with a lug 202 that is also mounted to the rod 
114. 
Referring to FIG. 5, a pair of recesses 204 are located 180 degrees apart 
in the bottom of the turntable 18. An air actuated motor 206, having an 
upwardly extending piston rod 208, is mounted to the base 14. A plunger 
210 is mounted to the top of the piston rod 208 and is in registry with 
whichever of the recesses 204 is located above the plunger 210 pursuant to 
the rotation of the turntable 18 in the manner described below. 
Referring to FIGS. 11-13, the tool section 12 includes a frame 212 in which 
an hydraulically operated motor 214 is mounted. The piston rod 216 of the 
motor 214 is connected to a slide 218 that is mounted for forward-rearward 
movement in the frame 212. Trunnions 220 on the slide 218 pivotally mount 
a yoke 222 for heightwise swinging movement about the horizontal axis of 
spindles 224 that are rigid with the yoke 222 and that are rotatably 
mounted in the trunnions 220. An air operated motor 226 is pivotally 
mounted on the slide 218 and has a piston rod 228 that is pivotally 
connected to a dependent arm 230 of the yoke 222 to thereby enable the 
motor 226 to effect heightwise swinging movement of the yoke 222 about the 
axis of the spindles 224. 
Referring to FIGS. 2 and 3, a hollow shaft 232 extends forwardly and 
rearwardly through the yoke 222 and is so mounted in the yoke 222 that it 
is rotatable about its longitudinal axis but is fixed against 
forward-rearward movement in the yoke 222. As shown in FIGS. 14 and 15, a 
fork 234, having a pair of forwardly extending tines 236 (see also FIG. 
1), is pivoted to a fork mount 238 that is anchored to the front of the 
shaft 232. 
Referring to FIGS. 16 and 17, a housing 240 is rotatably mounted for 
swinging movement about the longituding axis of the shaft 232 by means of 
a front trunnion 242 and a back trunnion 244 on the housing 240, the 
trunnions being so mounted to the shaft 232 as to be locked against 
forward-rearward movement on the shaft. An hydraulically operated motor 
246 is secured to a flange 248 that is rigid with one of the spindles 224. 
The piston rod 250 of the motor 246 is pivoted to the back of the housing 
240 whereby the motor 246 may effect lateral swinging of the housing about 
the axis of the shaft 232. 
Referring to FIGS. 16 and 18-20, a mount 252 is pivoted by pins 254 to the 
front trunnion 242 of the housing 240 for forward-rearward movement about 
the axis of the pins 254. A bar 256 on the mount 252 is located between a 
front stop 258 and a back stop 260 that are mounted to the front trunnion 
242. An electric motor 262 is rigidly secured to the mount 252 above the 
front trunnion 242. An air operated motor 264, mounted to the back 
trunnion 244, has a forwardly directed piston rod 266 that is pivoted to a 
bracket 268 secured to the mount 252 whereby the motor 264 can effect 
forward-rearward movement of the mount 252 about the axis of the pins 254. 
A housing 270 is rotatably mounted to the motor 262 for swinging movement 
about the axis of the motor 262. A tool holder 272, mounted to and 
extending forwardly of the housing 270, rotatably mounts a roughing tool 
in the form of a wire brush 274. The motor 262 and the brush 274 are 
driveingly connected by a belt 276 so as to enable the motor 262 to rotate 
the brush 274. As shown in FIG. 1, the brush 274 is located proximate to 
and between the fork tines 236. 
A counterweight assembly 276 (FIGS. 2 and 3) is affixed to the housing 270. 
An air operated motor 278 is interposed between the housing 240 and the 
counterweight assembly and is mounted to the housing 240 with the upwardly 
projecting piston rod 279 of this motor being connected to the 
counterweight assembly so that the motor 278 may effect heightwise 
movement of the brush 274 about the axis of the motor 262. 
Referring to FIGS. 16 and 17, a cam 280 is affixed to the shaft 232 between 
the trunnions 242 and 244. A lever 282 is pivoted between its ends to a 
flange 284 that is secured to the housing 240. A valve 286, mounted to the 
housing 240, has a spool 288 that is movably mounted in the body of the 
valve for movement towards and away from the top of the lever 282. The 
valve spool 288 is yieldably urged against the top of the lever 282 by 
pressurized air entering the valve 286. A cam follower 290, mounted to the 
bottom of the lever 282, is urged into engagement with the periphery of 
the cam 280 by the valve spool 288 under the influence of the pressurized 
air entering the valve 286. The valve 286 and the motor 246 are so 
connected to each other and to a source of hydraulic fluid as to form a 
servo follow up mechanism that is so constructed, in a known manner, that 
relative motion of the valve spool 288 with respect to the body of the 
valve 286 causes a corresponding extent of motion in one direction or the 
other of the piston rod 250 with respect to the motor 246. 
Referring to FIGS. 14 and 21, a bar 292 is mounted within the shaft 232 for 
forward-rearward movement. A sensing member 294 is mounted to a housing 
296 and is located beneath the folk tines 236. Rods 298, that are secured 
to the housing 296 and are mounted for forward-rearward movement in the 
fork 234, act to mount the sensing member 294 for forward-rearward 
movement in the fork 234. A head 300, that is mounted to the front of the 
bar 292, is in intersecting relationship with the back of the housing 296 
to thereby limit the extent of rearward movement of the sensing member 294 
in the fork 232. 
Referring to FIGS. 21 and 22, a flange 302 is mounted to the back of the 
shaft 232, a manifold 304 is mounted to the flange 302, and a valve 306 is 
rigidly secured to the manifold 304. The valve 306 has a valve spool 308 
that is reciprocably mounted in the valve 306 for forward-rearward 
movement. The front of the valve spool 308 is in alignment with a plunger 
310 that is mounted for forward-rearward movement in the valve 306. The 
plunger 310 is in alignment with a pin 312 that is secured to the back of 
the bar 292. The valve spool 308 is yieldably urged forwardly in the valve 
306 by a compression spring 314 that is interposed between a cap 316 at 
the back of the valve 306 and the back of the valve spool 308. 
The valve 306 and the motor 214 are so connected to each other and to a 
source of hydraulic fluid under pressure as to form a servo follow up 
mechanism so constituted, in a known manner, that forward-rearward 
movement in one direction or the other of the valve spool 308 with respect 
to the median position in the valve 306 shown in FIG. 22 causes 
corresponding motion in one direction or the other of the piston rod 216 
with respect to the motor 214. 
In the idle condition of the machine: the piston rod 32 is projected out of 
the motor 30 to place the stand 38 and the parts carried thereby, 
including the toe pad 50, the toe stop 66 and the finger 196 and the 
projection 198, relatively remote from the post 26 and the last pin 28; 
the piston rod 48 is retracted into the cylinder 46 to place the toe pad 
50 in a lower position; the piston rod 55 is retracted into the cylinder 
54 so that the brake pad 56 is spaced upwardly of the surface 58 of the 
slide 20; the piston rod 62 is projected out of the motor 60 to place the 
toe stop 66 in a raised position; the slide 20 is at one end of the 
turntable 18 with the bracket 86 bearing against the lug 202, with the 
finger 194 in engagement with the arm 170 and with the cam 172 swung 
against the force of the spring 174 so that the valve 180 is open; the 
last pin is in substantial alignment with the axis of rotation of the 
turntable 18, and the last pin 28 is in substantial forward-rearward 
alignment with the brush 274; the cam 123 is spaced from and out of 
engagement with the valve 122 and the valve 122 is open; the shaft 152 is 
rotating; the clutches 132, 140 and 146 are uncoupled so that the sprocket 
160 is being rotated about the stationary shaft 128 by the sprocket 156, 
the sprocket 166 is being rotated about the stationary shaft 138 by the 
sprocket 162, and the shaft 144 is stationary; the cams 182 and 184 are in 
the FIG. 6 position wherein the cam lobe 186 is engaging the valve 190 and 
the cam lobe 188 is disengaged from the valve 192; the piston rod 208 is 
projected out of the motor 206 with the plunger 210 inserted into one of 
the recesses 204 of the turntable 18 to lock the turntable against 
rotation; pressurized air is entering the valve 306 through a line 318 
(FIG. 22) and a port 320 to thereby move the valve spool 308 rearwardly 
against the force of the spring 314 to thus cause the servo follow up 
mechanism interconnecting the valve 306 and the motor 214 to retract the 
piston rod 216 into the motor 214 and thus place the slide 218, together 
with the fork tines 236, the roughing brush 274 and the sensing member 294 
in a rearward position; the piston rod 228 is projected out of the motor 
226 to thus place the fork tines 236, the roughing brush 274 and the 
sensing member 294 in an upper position; pressurized air is entering the 
body of the valve 286 to yieldably urge the valve spool 288 leftwardly 
(FIG. 17) against the top of the lever 282 while the cam 280 is causing 
the lever 282 to push the valve spool 288 to a median position in the body 
of the valve 286 to thereby cause the servo follow up mechanism connecting 
the valve 286 and the motor 246 to maintain the piston rod 250 in a median 
position in the motor 246 so that the fork tines 236 are in a 
substantially horizontal plane and the axis of rotation 322 (FIG. 18) of 
the brush 274 is in a substantially horizontal plane; the electric motor 
262 is operative to rotate the brush 274; the piston rod 266 is projected 
out of the motor 264 to thereby swing the mount 252, together with the 
brush 274, forwardly about the axis of the pins 254 to a position wherein 
the bar 256 engages the back 260 in which position the brush 274 is in a 
relatively forward position with respect to the sensing member 294; and 
the piston rod 279 is retracted into the motor 278 to thus position the 
brush 274 in a relatively elevated position with respect to the fork tines 
236. 
FIGS. 23 and 23A show a shoe assembly that comprises a last 324 having an 
upper 326 mounted thereon and an insole 328 mounted on its bottom. The 
upper 326 has been lasted so that the upper margin 330 lies against and is 
secured to the insole and extends inwardly of the periphery of the insloe 
and of the last bottom. 
The shoe assembly is mounted by the operator bottom-up on the last pin 28, 
with the last pin entering the conventional thimble hole in the top of the 
heel portion of the last, in such a manner that the toe end of the shoe 
assembly faces the stand 38. The operator then depresses the shoe assembly 
to lower a stem 332 (FIG. 7) and thus operate a valve 334. Operation of 
the valve 334 so actuates the motor 30 as to cause the piston rod 36 to be 
retracted into the motor 30 so as to move the stand 38, together with the 
toe pad 50, the toe stop 66, the finger 196 and the projection 198, 
towards the pest 26 under the yieldable force of pressurized air until the 
toe stop 66 engages the toe end of the shoe assembly. During this movement 
of the stand 38, the linkage formed by members 
88,92,94,96,98,102,104,106,108 and 110 enables the beam 100 and the cam 
123 to move in the same direction as the stand 38 towards the valve 122 at 
a faster speed than the speed of movement of the stand 38 for reasons that 
will be explained below. When the stand 38 has terminated its movement, 
the cam 123 is still spaced from the valve 122. The engagement of the toe 
stop 66 with the toe end of the shoe assembly causes the toe stop 66 and 
the lug 74 to swing clockwise (FIG. 7) about the axis of the pin 68 to 
thus cause the cam surface 78 to shift the valve 76. The shifting of the 
valve 76 actuates the motors 44, 52 and 60 so that the motor 44 raises the 
toe pad 50, the motor 52 lowers the brake pad 56 to press it against the 
surface 58 of the slide 20 and the motor 60 lowers the stop 66. 
The lowering of the toe stop 66 removes it from the periphery of the toe 
end of the shoe assembly so that it will not interfere with the roughing 
operation described below. The pressing of the brake pad 56 against the 
surface 58 locks the stand 38 in the position in the slide 20 it had 
assumed when the toe stop 66 engaged the toe end of the shoe assembly. The 
raising of the toe pad 50 under the yieldable force of pressurized air 
enables it to engage the forepart of the shoe assembly and tilt it about 
the last pin 28 until the last pin engages the periphery of the thimble 
hole in the last 324, thereby locking the shoe assembly to the slide 20 
for the below described roughing operation. 
The machine incorporates a construction similar to that shown in Pat. No. 
3,843,985 that enables the motors 44,52 and 60 to remain in actuated 
condition when the turntable 18 is rotated as described below. 
After the shoe assembly has been locked to the slide 20, the motor 226 is 
so actuated under the force of pressurized air as to retract the piston 
rod 228 into this motor and thus lower the shaft 232 to thereby lower the 
fork tines 236, the roughing tool 274 and the sensing member 294 about the 
axis of the spindles 224 until the fork tines 236 engage the upper margin 
330 in one of its breast line regions (FIGS. 24 and 24A), the shoe 
assembly being so located that the fork tines will intersect its bottom 
during their descent and the sensing member 294 will be located outwardly 
of the shoe assembly when the fork tines engage the shoe assembly. In 
response to the engagement of the fork tines 236 with the upper margin 
330, a valve 336 (FIGS. 14 and 15) is shifted in the manner disclosed in 
application Ser. No. 546,223 filed Feb. 3, 1975. The shifting of the valve 
336 causes the flow of pressurized air in the line 318 and the port 320 to 
be shut off thereby enabling the spring 314 to shift the valve spool 308, 
together with the plunger 310, the pin 312, the bar 292 and the sensing 
member 294 forwardly. This valve spool shifting actuates the motor 214, by 
means of the servo follow up mechanism interconnecting the valve 306 and 
the motor 214, to project the piston rod 216 forwardly to thus move the 
slide 218, together with the fork tines 236, the roughing tool 274 and the 
sensing member 294, forwardly. This forward movement is terminated when 
the sensing member 294 engages the side of the shoe assembly and then 
moves rearwardly in the fork 234 to thereby move the bar 292, the pin 312, 
the plunger 310 and the valve spool 308 rearwardly, the valve spool 308 
moving rearwardly against the force of the spring 314 until the valve 
spool arrives in the median position shown in FIG. 22 in the valve 306. 
The arrival of the valve spool 308 in the median position enables the 
servo follow up mechanism interconnecting the valve 306 and the motor 214 
to cause the motor 214 to terminate forward movement of the piston rod 
216. 
The shifting of the valve 366, after a time delay sufficient to enable the 
sensing member 294 to engage the side of the shoe assembly, also causes 
the motor 278 to project its piston rod 279 upwardly to thereby swing the 
roughing tool 274 downwardly about the axis of the motor 262 until 
radially projecting bristles 338 on the brush 274 engage the upper margin 
330 between the fork tines 236, as indicated in FIGS. 24 and 24A. 
The shifting of the valve 336, after the time delay referred to in the 
preceding paragraph, also actuates the motor 206 to move the plunger 210 
away from the recess 204 with which it had been in engagement to unlock 
the turntable 18 for rotation and actuates the clutch 140 to couple the 
rotating spocket 166 to the shaft 138 to thereby rotate the shaft 138. The 
rotation of the shaft 138, by way of the gears 134 and 136, effects 
rotation of the turntable 18 about the axis of the sleeve 16 to thus 
rotate the slide 20 and the shoe assembly about a center that is 
substantially in alignment with the last pin 28 and that lies 
approximately at the center of curvature, indicated by number 340 in FIG. 
23A, of the heel portion of the bottom of the shoe assembly. 
From the foregoing, it can be seen that the engagement of the fork tines 
236 causes a lowering of the rotating brush 274 into engagement with the 
upper margin 330 and a movement of the heel portion of the upper margin 
past the rotating brush. This arrangement enables the bristles 338 of the 
rotating brush 274 to abrade or rough the upper margin 330 as it is moving 
past the brush. 
During the movement of the heel portion of the upper margin past the 
rotating brush 274, as well as the movement of the other portions of the 
upper margin past the rotating brush as described below, the brush must 
move upwardly or downwardly in accordance with the elevation of the upper 
margin being roughed and must move forwardly and rearwardly so as to be 
positioned the desired distance inwardly of the outer periphery of the 
upper margin being roughed. In addition, the central plane of the brush 
274 which is at right angles to its axis of rotation, indicated by the 
chain line 342 in FIG. 24A, should be tilted during the movement of the 
portions of the upper margin being roughed past the roughing brush 274 so 
as to be at right angles to the plane of the portion of the upper margin 
330 being roughed. 
The upward and downward movement of the brush 274 during the movement of 
the upper margin past the brush is accomplished by virture of the fact 
that the brush is mounted to partake of the swinging movement of the yoke 
222 and is thus resiliently urged downwardly by the air operated motor 
226. 
The forward and rearward movements of the brush 274 during the movement of 
the upper margin past the brush is accomplished by the sensing member 294 
which is being resiliently urged forwardly against the side of the shoe 
assembly by the spring 314. The servo follow up mechanism connecting the 
motor 214 and the valve 306 is so constituted that the piston rod 216 is 
stationary to maintain the brush stationary in forward-rearward directions 
when the valve spool 308 is in a median position in the valve 306. A 
forward movement of the sensing member 294 by a portion of the side of the 
shoe assembly being displaced from the sensing member causes the valve 
spool 308 to move forwardly in the valve 306 to thereby cause the 
associated servo follow up mechanism to so operate the motor 214 as to 
move the piston rod 216 forwardly and thus move the brush 274 and the 
sensing member 294 forwardly until the sensing member again engages the 
side of the shoe assembly and thereby causes the bar 292 to move the valve 
spool 308 into its median position in the valve 306. A rearward movement 
of the sensing member 294 by a rearward pushing of the sensing member by a 
portion of the side of the shoe assembly causes the bar 292 to move 
rearwardly to push the valve spool 308 rearwardly in the valve 306 to 
thereby cause the associated servo follow up mechanism to so operate the 
motor 214 as to move the piston rod 216 rearwardly and thus move the brush 
274 and the sensing member 294 rearwardly until the side of the shoe 
assembly stops pushing the sensing member rearwardly so that the valve 
spool 308 regains its median position in the valve 306. 
The tilting of the central plane 342 of the brush 274 is accomplished by 
the mounting of the fork tines 236, together with the housing 240, for 
rotation about the axis of the shaft 232. During the movement of the upper 
margin 330 past the fork tines 236 that are being yieldably urged 
downwardly against the upper margin, the tines swing about the axis of the 
shaft 232 so that a plane connecting the bottoms of the tines is parallel 
to the plane of the upper margin engaged by the tines. This causes the cam 
280 to swing one way or the other and thus, through the lever 282, effect 
movement of the valve spool 288 one way or the other from a median 
position in the body of the valve 286. A movement of the valve spool 288 
in one direction or the other from its median position in the body of the 
valve 286 enables the servo follow up mechanism interconnecting the valve 
286 and the motor 246 to cause the motor 246 to move the piston rod 250 in 
a direction to swing the housing 240 one way or the other until the valve 
spool 288 is again in its median position in the body of the valve 286. 
The swinging of the housing 240 in a particular direction cause the brush 
274 to be swung in a corresponding direction until its central plane 342 
lies in a plane at right angles to the plane of the bottoms of the fork 
tine 236. 
As the shoe assembly rotates about the axis 340 the finger 194 becomes 
disengaged from the arm 170, thus enabling the spring 174 to cause the cam 
172 to close the valve 180, and the cam lobe 188 engages and closes the 
valve 192. When the shaft 138 has rotated 180 degrees from its starting 
position shown in FIG. 6, the cam lobe 186 is disengaged from the valve 
190 thereby permitting this valve to open. The opening of the valve 190 
actuates the pneumatic clutch 146 so as to couple the shaft 144 for 
rotation in unison with the shaft 152, deactuates the clutch 140 to 
thereby terminate the rotation of the shaft 138 and thus terminate the 
rotation of the turntable 18, and the motor 206 is actuated to bring the 
plunger 210 into engagement with a recess 204 to thus lock the turntable 
18 against rotation. From the foregoing, it can be seen that, after the 
turntable 18 has rotated 180 degrees to enable the heel portion of the 
upper margin 330 from one breast line portion to the other breast line 
portion to be roughed by the tool 274, the turntable 18, together with the 
shoe assembly, ceases its rotation and the shaft 144 is caused to rotate. 
The rotation of the shaft 144, by means of the gears 130, 142, causes the 
shaft 128 to rotate to thus rotate the gear 126 in a direction to linearly 
move the rack 124, together with the slide 20 and the shoe assembly, with 
respect to the stationary turntable 18 lengthwise past the brush 274 so 
that the brush 274 engages a first side portion 344 (FIG. 23A) of the 
upper margin 330 as the shoe assembly moves in a heel to toe direction 
past the brush 274 to thereby enable the brush to rough the first side 
portion 344 of the upper margin. This lengthwise movement of the shoe 
assembly in a heel to toe direction past the brush 274 continues until the 
finger 196 engages the arm 170 and the projection 198 engages the lug 200. 
The arm 170 at this time is in intersecting relationship with the finger 
196 due to the aforementioned disengagement of the finger 194 from the arm 
170 during the rotation of the shoe assembly about the axis 340. 
The aforementioned movement of the finger 1 and the projection 198 towards 
the post 26 by the motor 30 terminated when the toe stop 66 engaged the 
toe end of the shoe assembly and placed the finger 196 and the projection 
198 in a position wherein the approximate center of curvature of the toe 
portion of the shoe assembly, indicated by number 346 in FIG. 23A, is in 
registry with the axis of rotation of the turntable 18, formed by the axis 
of the sleeve 16, when the slide 20 completes its lengthwise movement on 
the stationary turntable 18 and the shoe assembly completes its movement 
in a heel to toe direction past the brush 274. The engagement of the arm 
170 by the finger 196 causes the cam 172 to open the valve 180. 
The opening of the valve 180 causes the motor 206 to move the plunger 210 
away from the recess 204 it had engaged to unlock the turntable 18 for 
rotation. The opening of the valve 180 also deactuates the clutch 146 to 
terminate the lengthwise movement of the slide 20 and of the shoe assembly 
in the turntable 18 and actuates the clutch 140 to again cause rotation of 
the turntable 18, the turntable now rotating about the axis 346 so that 
the toe portion of the upper margin 330 is swung past the brush 274 and is 
roughed. 
As the shoe assembly rotates about the axis 346, the finger 196 becomes 
disengaged from the arm 170, thus enabling the spring 174 to cause the cam 
172 to close the valve 180, and the cam lobe 186 engages and closes the 
valve 190. When the shaft 138 has rotated 180 degrees from its starting 
position to swing the toe portion of the upper margin 330 through a 180 
degree arc past the brush 274, the cam lobe 188 is disengaged from the 
valve 192 thereby permitting this valve to open. The opening of the valve 
192 causes the clutch 140 to be deactuated and causes the motor 206 to 
move the plunger 210 into engagement with a recess 204 to thereby 
terminate the rotation of the turntable 18 and to lock the turntable 
against rotation. 
The opening of the valve 192 also actuates the pneumatic clutch 132 to 
couple the rotating sprocket 160 to the shaft 128 to thereby rotate the 
shaft 128 and to cause the gear 126 to rotate in the opposite direction 
from which it was previously rotated in response to the actuation of the 
clutch 146. This rotation of the gear 126 moves the rack 124, together 
with the slide 20 and the shoe assembly, lengthwise past the brush 274 so 
that the brush 274 engages the second side portion 348 (FIG. 23A) of the 
upper margin 330 as the shoe assembly moves in a toe to heel direction 
past the brush 274 and the brush 274 thus roughs the second side portion 
348 of the shoe assembly. The lengthwise movement of the shoe assembly in 
a toe to heel direction past the brush 274 continues until the finger 194 
engages the arm 170 which is in intersecting relationship with the finger 
194 due to the aforementioned disengagement of the finger 196 from the arm 
170 during the rotation of the shoe assembly about the axis 346. The 
engagement of the arm 170 by the finger 194 causes the cam 172 to again 
open the valve 180. 
This opening of the valve 180 causes the deactuation of the clutch 132 to 
terminate the toe to heel movement of the shoe assembly past the brush 274 
and causes the machine parts to return to their idle positions and 
complete the machine cycle. The shoe assembly, with the roughed upper 
margin, is now removed from the machine. 
As shown, somewhat exaggeratedly, in FIG. 25, the bottom of the forepart of 
the shoe assembly, extending between the ball breaks 350 and 352 (FIG. 
23A) at the widest part of the shoe assembly bottom and the toe end 
extremity 354, is somewhat rounded and upwardly convex while the bottom of 
the shoe assembly is relatively horizontal and flat in a cross-section 
taken from side to side of the shoe assembly in the non-forepart portion 
of the shoe assembly, as shown in FIG. 24. in the forepart portion of the 
shoe assembly the bottom of the shoe assembly slopes upwardly as it 
extends inwardly of the periphery of the bottom of the shoe assembly. At 
the beginning of the roughing operation the brush 274 had been placed in a 
relatively forward position with respect to the sensing finger 294 by the 
motor 264 due to the piston rod 266 being projected out of this motor so 
that the bristles 338 would engage and rough the upper 330 a desired 
distance inwardly of the upper margin periphery. However, due to the 
inward and upward inclination of the upper margin 330 in the forepart 
portion of the shoe assembly, this relatively forward position of the 
brush 274 with respect to the sensing finger 294 would cause the bristles 
338 to engage the upper margin further inwardly of the upper margin 
periphery than it does in the non-forepart portion of the shoe assembly. 
In order to overcome this difficulty, the brush 274 is moved rearwardly 
relative to the sensing member 294 by adjusting means during the movement 
of the forepart portion of the upper margin 330 past the roughing brush 
274 in the manner described below. 
The valve 122 and the motor 264 are so connected to each other and to a 
source of air under pressure that when the valve 122 is open the piston 
rod 266 is projected out of the motor 264 to position the brush 274 in a 
relatively forward position with respect to the sensing member 294, as in 
the idle condition of the machine. When the valve 122 is closed by the cam 
123, as described below, the connections between the valve 122, the motor 
264 and the source of air under pressure are such as to cause the motor 
264 to retract the piston rod 266 to a position wherein the bar 256 
engages the front stop 258 in which position the brush 274 is in a 
relatively rearward position with respect to the sensing member 294. 
During the aforementioned heel to toe movement of the shoe assembly past 
the brush 274 to rough the side portion 344 of the upper margin 330 by the 
linear movement of the slide 20 with respect to the stationary turntable 
18, the cam 123 engaged the valve 122 to close the valve 122. The machine 
parts are so dimensioned that the valve 122 was closed by the cam 123 when 
the upper margin in the region of the ball break 352 was being engaged and 
roughed by the brush 274. The valve 122 stayed closed during the remainder 
of the heel to toe movement of the shoe assembly, during the rotation of 
the turntable 18 about the axis 346 wherein the toe portion of the upper 
margin 330 was roughed by the brush 274, and during the early part of the 
toe to heel movement of the shoe assembly past the brush 274 to rough the 
side portion 348 of the upper margin by the linear movement of the slide 
20 with respect to the stationary turntable 18. The machine parts are so 
dimensioned that the cam 123 became disengaged from the valve 122 to 
enable the valve 122 to reopen when the upper margin in the region of the 
ball break 350 was being engaged and roughed by the brush 274. Therefore 
the cam 133 and the valve 122 and the connections between the valve 122 
and the motor 264 act as the aforementioned adjusting means to move the 
brush 274 rearwardly relative to the sensing finger 294 during the 
movement of the forepart portion of the upper margin 330 past the roughing 
brush 274. 
In the idle position of the machine, the stand 38 is in an idle stand 
position and the cam 123 is in an idle cam position. Pursuant to the 
operation of the motor 30, the projection 198 and the cam 123 are each 
moved in a toe to heel direction with respect to the shoe assembly until 
these movements are terminated by the engagement of the toe stop 66 with 
the toe end of the shoe assembly at which time the stand 38 is in a stand 
working position and the cam 123 is in a cam working position. For a 
particular shoe assembly, the extent of the heel to toe and toe to heel 
linear movements of the shoe assembly past the brush 274 is equal to the 
distance in heel-toe directions between the projection 198 when the stand 
38 is in its working position and the lug 200. For a particular shoe 
assembly, the extent of linear heel to toe movement of the shoe assembly 
past the brush 274 before the actuation of the brush adjusting means 
caused by the engagement of the valve 122 by the cam 123 is equal to the 
distance in heel-toe directions between the cam working position and the 
valve 122. For a particular shoe assembly, the extent of linear toe to 
heel movement of the shoe assembly past the brush 274 after the 
deactuation of the brush adjusting means by the disengagement of the cam 
123 from the valve 122 is also equal to the distance in heel-toe 
directions between the cam working position and the valve 122. 
In changing the machine from operation on a first shoe assembly to a second 
shoe assembly having a different overall length than the first shoe 
assembly, the distance in heel-toe directions between the projection 198 
in the working position of the stand 38 and the lug 200 is greater for the 
second shoe assembly than for the first shoe assembly, if the second shoe 
assembly has a greater overall length than the first shoe assembly, and 
this distance is less for the second shoe assembly than for the first shoe 
assembly, if the second shoe assembly is shorter than the first shoe 
assembly, by amounts that are equal to the increase or decrease in overall 
length of the second shoe assembly with respect to the first shoe 
assembly. Therefore, the extent of heel to toe and toe to heel linear 
movements of the second shoe assembly past brush 274 is increased or 
decreased relative to the corresponding movements of the first shoe 
assembly by an amount that is equal to the increase or decrease in length 
of the second shoe assembly with respect to the first shoe assembly. 
The increase or decrease of the heel-toe length of the forepart portion of 
the second shoe assembly from the corresponding portion of the first shoe 
assembly is less than the increase or decrease of the overall length of 
the second shoe assembly from the first shoe assembly. Therefore, the 
increase or decrease in distance between the cam working position and the 
valve 122 for the second shoe assembly relative to the first shoe assembly 
should be more than the increase or decrease in the overall length of the 
second shoe assembly with respect to the first shoe assembly. In order to 
establish this relationship in the change in distances between the 
projection 198 in the stand working position and the lug 200 and between 
the cam working position and the valve 122 when changing the overall 
length of the shoe assembly, the motor 30 moves the cam 123 towards the 
valve 122 at a faster speed than it moves the stand 38 and the projection 
198 towards the post 26 and the lug 200. 
There follows a recapitulation of the machine parts and the mode of 
operation of the machine that are pertinent to this invention. 
The machine is intended to rough the margin 330 of the upper 326 of the 
shoe assembly comprised of the last 324 having the insole 328 located on 
its bottom and the upper 326 mounted thereon with the upper margin lying 
against and being secured to the periphery of the insole. The machine 
comprises the frame 212, the housing 240 mounted for forward-rearward 
movement with respect to the frame, the roughing tool 274 mounted to the 
housing for forward-rearward movement with respect to the housing about 
the axis of the pins 254, drive means comprised of the motor 264 for 
moving the roughing tool between forward and rearward positions with 
respect to the housing, the table 18, the slide 20 mounted to the table 
for movement with respect to the table, a shoe assembly support comprised 
of the last pin 28 and the toe pad 50 for supporting the shoe assembly 
bottom-up, and shoe assembly support moving means shown in FIG. 4 that 
includes means comprised of the rack 124 and the gear 126 for moving the 
slide with respect to the table to thereby move portions of the upper 
margin past the housing 240 and the roughing tool 274. Operating means 
comprised of the motor 226, the sensing member 294 and the servo follow up 
mechanism connecting the motor 214 and the valve 306, are effective during 
the movement of the upper margin portions past the housing 240 to so move 
housing forwardly and rearwardly as to maintain the housing in a 
prescribed forward-rearward relationship with respect to the periphery of 
the side of the shoe assembly moving past the housing so as to enable the 
roughing tool 274 to engage the upper margin 330 a relatively great 
distance inwardly of the periphery of the shoe assembly bottom when the 
roughing tool is in said forward position and to enable the roughing tool 
to engage the upper margin a relatively small distance inwardly of the 
periphery of the shoe assembly bottom when the roughing tool is in said 
rearward position. A control member, in the form of the valve 122, is 
mounted to the table 18 and an actuating member, in the form of the cam 
123, is mounted to the slide 20, these members being so constructed and 
arranged to be in intersecting relationship or non-intersecting 
relationship during the movement of the upper margin portions past the 
housing 240 and the roughing tool 274 caused by the movement of the slide 
20 with respect to the table 18 during the operation of the shoe assembly 
support moving means. Adjusting means so connect the control member and 
the actuating member to the drive means as to place the roughing tool in 
one of its position when the members are in non-intersecting relationship 
and to place the roughing tool in the other of its positions when the 
members are in intersecting relationship. 
The table 18 is in the form of a turntable mounted for rotary movement 
about the upright axis of the sleeve 16. The slide 20 is mounted to the 
turntable for reciprocal movement in two opposite prone directions between 
two end positions on the turntable. The shoe assembly support moving means 
comprises means including the clutch 146 for first moving the slide with 
respect to the turntable while the turntable is stationary in a first of 
said directions between said end positions so as to move a first side 
portion 344 of the upper margin 330 past the roughing tool 274 in such a 
manner that relative movement extending from the heel of the shoe assembly 
towards the toe of the shoe assembly of the roughing tool with respect to 
the upper margin takes place, means including the clutch 140 for 
thereafter rotating the turntable 18 180 degrees while the slide 20 is 
stationary relative to the turntable to move the toe portion of the upper 
margin past the roughing tool 274, and means including the clutch 132 for 
thereafter moving the slide with respect to the turntable while the 
turntable is stationary in the other of said directions between said end 
positions so as to move the other side portion 348 of the upper margin 
past the roughing tool in such a manner that relative movement extending 
from the toe of the shoe assembly towards the heel of the shoe assembly of 
the roughing tool with respect to the upper margin takes place. The 
control and actuating members are so constructed and arranged that the 
members are in non-intersecting relationship at the commencement of the 
slide movement in said first of said directions, the members are placed in 
intersecting relationship during the slide movement in said first of said 
directions, the members remain in intersecting relationship during the 
turntable rotation and after the commencement of the slide movement in 
said other of said directions, and the members are placed in 
non-intersecting relationship during the slide movement in said other of 
said directions. The adjusting means is so constructed and arranged as to 
cause the drive means 264 to place the roughing tool 274 in its forward 
position when the members are in non-intersecting relationship and to 
cause the drive means 264 to place the roughing tool 274 in its rearward 
position when the members are in intersecting relationship. The control 
member constituted by valve 122 forms a normally open regulator that is 
movable between open and closed positions. The actuating member 
constituted by the cam 123 is so constructed and arranged as to engage and 
thereby cause the regulator to move to its closed position during the 
movement of the slide 20 in said first of said directions and to disengage 
the regulator and thereby enable the regulator to move to its open 
position during the movement of the slide in said other of said 
directions. The adjusting means is so constructed and arranged as to cause 
the drive means 264 to place the roughing tool 274 in its forward position 
when the regulator is in its open position and to cause the drive means 
264 to place the roughing tool in its rearward position when the regulator 
is in its closed position. 
The post 26 is rigidly mounted to the slide 20 and a backpart shoe assembly 
supporting element, constituted by the last pin 28, for supporting the 
backpart of the shoe assembly is mounted to the post. The stand 38 is 
mounted to the slide 20 for movement towards and away from the post 26 and 
a forepart shoe assembly supporting element, constituted by the toe pad 
50, for supporting the forepart of the shoe assembly is mounted to the 
stand. The motor 30 forms means for moving the stand towards the post from 
an initial stand position to a working stand position through a distance 
that is innersely proportional to the length of a shoe assembly that is 
supported on the backpart supporting element to thereby enable the 
forepart supporting element to be placed in a supportive position with 
respect to the forepart of the shoe assembly. This distance is determined 
by the engagement of the toe stop 66, that is mounted to the stand 38, 
with the toe end of the shoe assembly. The projection 198 mounted to the 
stand 38 and the lug 200 mounted to the turntable 18 constitute 
cooperative terminating means that define the end position reached at the 
end of the movement of the slide 20 with respect to the turntable 18 in 
said first of said directions referred to above. The actuating member 
constituted by the cam 123 is mounted to the stand 38 for movement in 
unison with the movement of the stand towards the post 26 from an initial 
actuating member position to a working actuating member position. 
The actuating member constituted by the cam 123 is so mounted that the 
distance between the initial and working actuating member positions is 
greater than the distance between the initial and working stand positions. 
This is accomplished by providing connecting means that so connect the 
actuating member to the stand and to the turntable as to cause the 
actuating member to move from its initial position to its working position 
at a greater speed than the speed of movement of the stand from its 
initial position to its working position. This connecting means comprises 
the plate 84 rigidly connected to the stand 38 for movement in union 
therewith, the beam 100, to which the cam 123 is affixed, mounted to the 
plate for movement with respect to the plate towards and away from the 
regulator constituted by the valve 122, and a linkage constituted by the 
members 88, 92, 94, 96, 108 and ll0 so connecting the slide 20, the plate 
84 and the beam l00 as to enable the movement of the stand 38 towards the 
post 26 to cause movement of the cam 123 towards the regulator at a 
greater speed than the speed of movement of the stand towards the post.