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Aug-20,1946.
G. CLAUSING
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1
2,405,941
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. 19, 194sv
9 sheets-sheet 1
GeorgeINVENTOR‘
Clausmg
BY
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Aug. 20, 1946.
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2,495,941
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. 19, 1943
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- INVENTOR
George Ceclusmg
Aug, 20, 1946.,
G. CLAUSING-
2,405,941‘
AUTOMATIC HEEL TURNING MACHINE
Filgd Oct. 19,1943
9 Sheets-Sheet 4
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INVENTOR
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George Clousmg
Aug- 20» 1946-
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G._CLAUSING
2,4®5,41
AUTOMATIC HEEL TURNING MACHINE
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Filed Oct. 19, 1943
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9 Sheets-Sheet 5
‘
INVENTOR. _ '
G eorg e' Clqusmg
Aug. 20, 1946.
G. CLAUSING
2,405,941
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. '19, 1943 ‘
.9 Sheets-Sheet '6
INVENTOR
‘- George Ciausmg
Aug.>20, 1946.
2,405,941
_ G. CLAUSING‘
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. 19', 1945
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INVENTOR' ‘
George. Clausmg
BY
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vAug, 20, 1946.
'
G. cLAuslNG
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2,405,941 '
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. 19, 1945
9 Sheets-Sheet 8
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George. Cluusmg
Aug. 20, 1946.
_
2,405,941
G. CLAUSING
AUTOMATIC HEEL TURNING MACHINE
Filed Oct. 19,1943
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INVENTOR:
George 'Cl?usmg
Patented Aug. 20, 1946
2,405,941
STATES
TEN
orrics
2,405,941
AUTOMATIC HEEL TURNING MACHINE
George Clausing, Portsmouth, Ohio, assignor to
Vulcan CorporationlPortsmouth, Ohio, a cor
poration of Ohio
Application October 19, 1943, Serial No. 566,871
1
29 Claims.
This invention relates to an apparatus for au~
tomatically forming a plurality of identically
shaped objects by means of a cutting operation
executed by a rapidly rotated formed cutter blade.
More particularly it is directed to a machine for
shaping heels for shoes.
,
(01. 12-—87)
2
There are two cutter manipulating assemblies as
above described of like construction one of which
executes the desired out along one side of the
heel from its breast corner rearwardly to the
heel back line. The other mechanism is dis~
posed upon the opposite side of the carrier mem
known
The operation
in the heel
performed
making art
by the
as heel
apparatus
turning.
ber and functions to shape the other side of the
heel. Some types of heels such as those ‘which
Speci?cally the operation is that which results
in imparting to the heel its general external con- 10 the heel manufacturer considers to be a low heel
may be made upon the machine as above de
figuration by shaping those areas thereof that
scribed. To produce other types of heels for ex
extend along its sides and back.
ample those considered to be high heels further
Not only is it the present practice butit has
manipulation
of the relative movements between
been the practice of heel makers for many years
to perform the turning operation upon a hand 15 the cutters and the block must be introduced to
obtain the desired heel form. To execute this
operated machine whose chief characteristics are
further manipulation, the present invention in
those of a standard spindle shaper such as that
troduces an additional controlled motion of the
used generally in the wood working art. The
block itself with respect to the carrier member
main difference being that the commonly used
heel turning machine is provided with a mecha- 20 during the cutting operation. This additional
movement of the heel block is made possible by
nism for holding a heel block and enabling an
an especially constructed block holding jack in
operator to present the block to the cutter under
which a block clamping member is relatively mov
the guidance of a form. To produce a quantity
able with respect to the jack as a whole.
of heels of satisfactory quality upon such a ma
The motion imparted to the block takes place
chine a skilled operator must be employed. The 25
in a plane parallel to the heightwise heel axis and
operator moreover was able to turn only a lim
to the direction of its travel. The motion impart
ited number of heels in a working day. His ca
ed to the block is or" the nature of a rocking or
pacity was limited by the natural factor of fatigue
oscillating movement derived from a cam and ~
which also seriously interfered with the pro
duction of uniformally high quality in his work.‘ ' follower device so arranged that the movement
of the carrier imparts a predetermined motion to
The present invention transforms the turning
a member ‘movable upon the carrier which in turn
operation from a relatively slow inaccurate proc
successively transmits the movement to the
ess to a rapid mechanically precise operation in
blocks through a mechanical connection to the
dependent of the human factors above men
block clamping elements of each jack during the
tioned. The apparatus consists essentially of a . heel shaping operation.
'
base or supporting element upon which a car
Means
are
provided
for
releasing
the
proc
rier member is movable mounted. The carrier
essed heels from the jacks and maintaining suc
member has a plurality of heel block holding
ceeding vacated jacks in condition to again re~
jacks mounted thereon arranged to move rough
ceive an uncut block. An important feature of
heel blocks into cutting relation with rapidly ro
the invention which will be described in detail
tated cutter blades to execute the forming oper
ation.
The cutter blades are mounted upon a
spindle which desirably may have an electric
motor direct connected thereto. The cutter
spindle is received in a swinging bracketpivoted
upon the base member in such position that the
cutters may move into the path of travel‘ of the
heel blocks as they are fed along by the carrier
member. The brackets and cutters are swung
toward the carrier by a suitable means such as r
a weight and cable device.
The inward move
ment of the cutter during the turning operation
is positively controlled by a cam and follower
mechanism designed accurately to execute a pre
determined heel contour.
55
hereinafter resides in the especially designed ar~
rangement of the elements which move the cut
ter into cutting relation with the heel block and
cause it to follow around the heel to the back
line thereof where the cutting action is discon~
mounted
tinued. is
The
so positioned
pivot upon
with
which
respect
theto cutter
the path
of travel of the blocks that the linear speed 01'
the progress of the out along the block at the cut
ting line is held within predetermined limits.
Such speed normally would be substantially con
stant or it may be desirable to gradually decrease
the speed from the side of the heel around the
corner of the block and attaining minimum speed
at the back line.
'
'
2,405,941
3
To present a better understanding of the in
vention a particular embodiment thereof will
now be described in connection with the accom
panying drawings in which:
Fig. l is a front elevation of the apparatus.
Fig. 2 is an enlarged detailed view of the cam
device employed to control the bodily movement
4
half of the heel is ?rst completed by feeding a
rough block into cutting engagement with a ro
tating cutter. The cut is initiated at a corner
of the heel breast, proceeds along one side of the
heel and half way around the back of the heel
ending at a line upon a central longitudinal plane
through the heel known as the back line. A sim
ilar procedure is executed upon the other side
of the cutters.
'
of the heel block by another cutter to complete
Fig. 3 is a partial side view of the apparatus
the turning operation. The cutters are shaped to
on the line 3-3 of Fig. 1 showing the conveyor 10 produce the desired heel pro?le contour while a
wheel in cross section.
-
Fig. 4 is an enlarged detailed side View of a
form plate or cam acts to control the relative
position of the cutter and the block during the
portion of the conveyor wheel‘ illustrating the
cutting operation thereby to produce a predeter
construction and operation of the means for rock
15 mined heel seat outline.
ing the heel block.
The preferred form of the invention illustrated
Fig. 5 is a cross section on line 5-5 of Fig. Ll
is provided with a rigid supporting frame is upon
showing in enlarged detail the ‘construction and
which all of its elements are mounted. A con
method of mounting the rocking lever for rock
veyor or carrier is provided for automatically
ing the heel block.
feeding
heel blocks into position to be processed.
Fig. 6 is a cross section on line i§-Ei of Fig. 1 20 The carrier may be of any suitable construction.
showing in enlarged detail the construction and
A desirable form of carrier is shown wherein a
operation of one of the jacks.
plurality of heel jacks I9 are mounted upon the
Fig. '7 is a detailed view illustrating the means
periphery of a circular carrier wheel 26. The
for applying clamping pressure to retain the heel
wheel 20, as shown in Fig. 3 is mounted upon
blocks in their jacks.
the end of a rigid shaft 2| horizontally mounted
Fig. 8 is an illustration of vthe cam system em
upon the machine frame l8. Desirably the shaft
ployed for releasing the clamping pressure from
is supported upon anti-fraction bearings 22.
the heel blocks after the turning operation has
While the machine is in operation the carrier
been executed.
is driven constantly at uniform speed determined
Fig. 9 is a plan view of the elements shown in 30 by, the number of heel blocks the operator is ca
Fig. 2 and illustrates the relationship between
pable of feeding to the jacks. Any suitable means
the cam and follower which acts to determine the
may be used to drive the wheel.
One such means
heel shape.
of driving the wheel is shown in Fig. 3, wherein
Figs. 9-—A, 9--B, and 9—-C are views similar
shaft 2! is rotated by motor 23 through the
to that of Fig. 9 showing various positions of the 35 the
medium of a speed reducing unit 24. The con
cutter, cam and follower at various stages of the
nection from the unit 2d to the shaft 2| is made
cycle involved in cutting a heel block.
through a friction clutch 25 having an operating
Fig. 10 is a diagrammatic view illustrating the
handle 25 by means of which the wheel 20 may
relative path of movement of the cutter and cut
be started and stopped independently of the driv
ter arm with respect to the heel block during the
ing motor.
turning operation.
There are two power driven cutter assemblies
the
motor
and
cut
Fig. 11 is a general view of
each mounted upon opposite sides of the plane of
ter unit supporting bracket.
.
the carrier. A desirable means for driving the
Fig. 12 is a plan view of the elements shown
cutters is illustratedin Fig. 1 wherein the cutter
45
in Fig. 11 with a portion shown in section to illus
heads 21 are mounted directly upon the spindles
trate an angular adjustment device.
of their driving motors 28. The motors and cut
Fig. 13 is a detailed view illustrating the driv
ters are adjustly mounted upon supporting brack
ing means forswinging the cutter and motor
ets 29. The cutters and their driving motors are
supporting arm.
.
so mounted upon the machine frame that their
Fig. is is a general view of the machine frame 50 axes are substantially radial with respect to the
broken away to show the mechanism employed to
axis of the shaft 2|. Each cutter is spaced angu
swing the motor and cutter brackets vintoopera
larly about the shaft axis at an angle at least as
tive position.
great as the angle of separation between adja
Fig. 15 is a detailed illustration showing the
cent heel jacks I9.
chain and sprocket connection between the op 55
To perform the turning operation the cutters
erating weights and the pinion shaft for the mo
2'! must be fed inward toward the carrier 20.
tor and cutter bracket drive.
To obtain this motion any suitable means may be
It is important to note in connection with the
employed. However, the direction of travel and
following description that the mechanism em
the character of this inward motion of the cutter
60
bodied in the apparatus presented is highly effi
must be controlled to properly execute the turn
cient and rapid in operation and moreover pre
ing operation. The present invention provides a
sents a design having basic simplicity which in
very effective and positive means for co-relating
sures a long uninterrupted life of consistently
the motion of the cutter with the travel of the
accurate operation.
‘
heel block throughout the cutting operation. The
The operation of turning heels is highly critical 65 mechanism for obtaining this desirable co-action
and precise in character and as above suggested
between cutter and block is an important feature
the operation has required the services of highly
of the invention. To obtain maximum produc
skilled operators who use a converted type'of
tivity and high quality of product the linear speed
spindle shaper wherein the heel blocks are se
of the out as it progresses along the line of cut 30
70
.cured in a pivoted jack and are fed to the cutters
upon the block 3| as shown in Fig. 10, must be
by hand. The present invention eliminates the
regulated. It has been found that a too rapid
. inaccuracies and lack of high‘ volume productivity
traverse of the cutter along the back surface of
of the present method.
Brie?y the operation of turning a heel involves
the execution of two similar operations. One-'
. the block where the cutter is cutting across the
wood grain and removing a relatively large vol
5
2,405,941
time of wood as the corner of the block is re—
moved, causes a poor quality of workmanship on
the heel. The severity of such a cut over-loads
the driving motor and imposes too great a cutting
pressure upon the heel block. These and other
6
shown by successive dotted circles. The opera
tional result is the same regardless of which of
the elements moves. The cumulative effect of
the complete operation is illustrated by the out
line of the out upon the block 3! represented by
abnormal conditions arising out of an excessively
the line 39. ‘The circles representing successive ,
severe cut causes vibration and springing of the
‘positions of the shaft 32 are equally spaced reps
parts which result in air inaccurate and roughly
resenting uniform rate of travel. By noting the
cut surface.
spacing between corresponding positions ~of the
In the attempts which have heretofore been
axis of the cutter which falls on the line 35, it will
made to produce a machine of the type herein
be noted that the rate of travel of the cutter axis
presented. no satisfactory control of the relative
decreases Slightly around the curve. At the com
motion between the cutter and block has been
pletion of the cutting operation of one cutter
devised.
mechanism, the other mechanism upon the other
The speed and character of the translational 15 side of the carrier then goes into action and com
movement of the cutter as it progresses along the
pletes the turning operation upon the other side
heel block in the present invention is determined
of the heel block in the same manner. To de
by two factors. First the peripheral speed of the
crease the speed of travel of the cutter along the
carrier wheel 2% and secondly the inward travel
heel block toward the rear portion of the heel,
of the cutter head. The inward swing of the 20 the angle between the plane 3:? and the line drawn
heel curve complicates the control of the move
through the axis of the shaft 32 and the cutter
ment of the cutter along the line 38 representing
axis may be increased by moving the shaft 32
the contour of the heel seat as shown in Fig. 10.’
outward from the carrier. This may be done
To produce an e?icient result one or the other
in any manner as by shifting the position of the
or both of these factors must be subjected to a 25 screws which hold the bearing members 33 into
control of predetermined character. For exam
new positions 33K (Fig. 9).
ple, without such control assuming the peripheral
The setting of the bearing members 33 in the
speed of the carrier were maintained constantly
position shown in Figs. 9, 9—~A, 9-13 and 9-C,
uniform and the cutter was permitted to move
or in the position 33:0, predetermines the rate of
directly inward at right angles to the path of the 30 travel of the cutter 2? along the curved and back
blocks in the jacks, the speed of the cut at the
portion of the heel block 3!, assuming a given
side of the heel would be normal, but at the
distance between the axes of the cutter and shaft
corner of the block and at the back of the heel
32 and that the block 3i moves at a constant
the inward travel of the cutter would of necessity
predetermined rate. The turning operation is
be so excessively rapid as to be impractical for 3, effected as a heel block 3! advances to the left,
reasons given above.
the cutter being at the successive positions around
In view of the fact that in a high volume pro
the block 3! at equal intervals of time, as shown
duction machine it is highly desirable to operate
in Fig. 10. As the cutter moves around the block,
the carrier uninterruptedly and at uniform speed,
it begins to follow the block, thus increasing the
the present invention maintains the movement 40 angle of the line drawn through the aXes of the
of the carrier uniform and introduces the neces
cutter and shaft 32 with respect to the path of
sary control to the inward motion of the cutter
movement of the block 3i, as clearly shown in
head. A satisfactory regulation of the rate of
Fig. 10. In this ?gure of the drawings, the suc_
travel of the cutter along the cutting line 3Q calls
cessive dotted circles of the shaft 32 represent
for maintaining the rate of travel substantially 43 equal time intervals, and the same is true of the
uniform throughout the cut or for a decrease in
successive circles 2'! representing the cutter. The
rate at the back of the heel. Any suitable means
distance traveled by the cutter along the curved
may be employed to obtain control of movement
line Si‘! in each of these successive intervals may
of the cutter. A very ingenious and'eifective
be determined approximately from the distance
means is shown herein. The motor brackets 29
between corresponding points on the circles along
are pivotally mounted upon the machine frame
the line til, from which it will be apparent that
upon shafts 32 disposed substantially parallel to
the rate of travel of the cutter around the curve
the axis of the cutters and at a substantial dis
of the line 3s and along the back of the block
tance away from the plane in which the heel
3! to the back line 36, is somewhat less than that
blocks 3i move. The shafts are supported in
along the upper portion of the line 313, which is in
bearings 33 ?xed upon the machine frame. The
a plane substantially parallel to the plane of the
position of the shafts 32 as shown in Fig. 9 is
line of travel of the block 3!. If the shaft 32
such that a line drawn between the axis of the
were moved nearer the line 313 (Fig. 9) less time
shafts and the axis of the cutters during the
would be available for cutting the curved and rear
cutting operation lies at an angle between 30° and 60 portion of the heel block than in the positions
60° with respect to the plane as in which the
shown in Figs. 9 and 10.
blocks travel. Fig. 10 shows this angular rela
The means employed to impart the desired seat
tionship and also the fact that the angle increases
outline to the heel as represented by the line 39
as the cutting operation on a particular heel blockv
is best shown in Figs. 9, 9—A, 9—-B and 9-0. To
proceeds.
‘ 65 more clearly illustrate the mechanism only the
Referring to Fig. 10, the position and path of
main elements are shown. Inasmuch as the ele
travel of the elements is diagrammatically illus
ments for forming both sides of the heel are ‘of
trated. To more clearly show the movement of
identical construction only one mechanism will be
the parts in this diagram the block is shown sta
described. The motor and cutter bracket 29 and
tionary and the cutter supporting shaft 32 is 70 the cutter 2?. are shown in dotted lines. In the
shown as if it were moving by a series of dotted
position of the parts illustrated in Fig. 9 the cutter
positions. Also the movement of the cutter 2?
has completed its operation and further move
is illustrated by a series of dotted positions, suc
ment of the carrier 26 causes the cutter to be
cessive positions of the cutter corresponding to
successive relative positions of the shaft 32 as
withdrawn to the outer portion of the cutting
zone by reason of engagement of the roll 31 with
2,405,941
'7
the cam 38. The cam 38 is rigidly secured to a
‘cam supporting arm 39 rigidly secured upon the
lower end of the shaft 32. The bracket 23 is
keyed to the shaft 32 with the result that move
ment of the arm 39 moves the cutter and bracket.
Follower rolls 31, as shown in Figs. .1 and 3, are
secured upon opposite sides of the carrier 20 at its
periphery. A pair of these rolls are provided for
each heel jack and are rotatably received upon
supporting members All rigidly secured to the
carrier 20. The rolls are accurately positioned
about the periphery of the carrier at the same
angular intervals as that of the heel jacks.
Any suitable means may be provided for sup
plying the motive power to move the cutter heads .
into cutting relation with the blocks and to main
tain the controlling cam in engagement with the
follower rolls 31. Desirably such means should
exert a resilient force. An e?icient arrangement
is illustrated in Figs. 14 and 15, in which inertia .
means are provided for obtaining the necessary
power. A weight 4| is provided for each cutter.
The weights are attached to cables 42 which are
led over directional pullies 43 and attached to
short lengths of sprocket chain 44 which in turn
are secured to and have driving engagement with
sprockets 45 ?xed upon one end of shafts 46 ro
tatably mounted in the machine frame l8. The
other end of the shafts 481 have ?xed thereon
pinion gears 41 which in turn mesh with the teeth
of segments 48 shown best in Fig. 13. Segments
48 are keyed to the shaft 32 and desirably are en
closed in casings 49 to exclude dirt, chips and all
foreign matter from the mechanism. The
weights ill therefore, serve to urge the cutters
into cutting relation with the blocks through the
intermediary of the above described mechanism.
It should be pointed out in connection with
so as to bring the follower rolls 31 successively
into contact with the cams 38 and 50. The en
gagement of the rollsection of large diameter
with the cam 33 causes the cutter to move out
ward with respect to the carrier and to bring it
into a position for starting a cutting operation
on a heel block. Fig. 9 illustrates the position of
the cutter 21 at the end of a cutting operation
on the cross-hatched heel block 3!. It will be
noted that the cutting line 3% has been formed
from the breast corner around to the back line
35, and that the cam 38 has just moved into en
gagement with the large diameter portion of a
succeeding follower roll 31. In this position, the
curved edge 53 of the cam 50 still rests on the
small diameter portion of the follower roll 31
opposite the cross-hatched block 3|.
Fig. 9—A of the drawings shows the position
of the elements shown in Fig. 9 after the cross~
hatched block 3i has been moved substantially
away from the cutter 21. It will be noted that
in Fig. 9-—A the large diameter portion of the
‘ only'follower roll 31' now operating on the cutter
arm, has moved along the inclined edge of the
cam 33 to bring the cutter 2'! out somewhat to
ward a position for starting the cutting operation
on a new heel block 3!.
Fig. 9-—B shows the
position of the cutter and the cams just after
the cutting operation on the heel block started.
In this ?gure it will be noted that the follower
roll 31, acting on the cam 38 in Fig. 9—A. has
been moved to a position where the shaping cam
59 has taken over control by engaging the small
diameter section of the follower roll. A subse
quent stage in the cycle of cutting a heel block
is shown in Fig. 9—~C of the drawings, in which
the cutter 21 is shown just around the back of
the curve of the cutting line 30, while the fol
lower roll 31 opposite the block 3|, has moved
40 substantially along the edge 53 of the pattern
cam 58. The position at the completion of the
cutting cycle is the same as in Fig. 9.
Shortly after the end of each cutting operation,
this type of resilient motive power that a smooth
and uniform out is assured. Pressure of the
cams upon the followers remains constant and
moreover a still more important condition is
maintained. The tendency of the cutter to
a succeeding follower roll 31 engages the cam 33
bounce away from the block during the cutting
operation is reduced to a minimum. The sudden 45 to restore the cutter 2‘! to its initial position for
starting a cutting operation on a new heel block.
application of the force of the cutting blades
After one side of a heel block has been cut in the
upon the block sets up a reactive force tending
manner described above, the other side of the
to move the cutters away from the cut. This
block is‘cut by a similar cycle of operation by
tendency of the cutters to move away from the
cut is resisted not alone by the steady pull of 50 the cutter on the other side of the carrier 20,
which has its own cams for successive engage
the weight vbut by a greater force set up by the
ment with the spaced follower rolls 31 on the
inherent inertia of the weight. All reactive
opposite side of the carrier 20.
forces are snubbed out by the weights while the
For certain types of heels the above cycle of
inward movement of the cutter head is effected
55 movement between cutters and blocks is suffi
by the pull of the weights due to gravity.
cient to produce a satisfactory heel. For many
The follower rolls 31 have two sections, an
other types of heels, however, it becomes neces
outer section of small diameter and an inner
sary to introduce additional relative movement
section of large diameter, the latter of which
between the blocks and cutters. For example,
engages the edge of the cam 38. The section of
small diameter engages a shaped cam 50 which, 60 in a relatively high heel, the shape of its top
lift end varies substantially from its heel seat
like the cam 38, is rigidly secured to the cam
outline. To produce this desired heel contour
support arm 39. The shaped cam 50 is provided
the heel blocks are given a rocking motion while
with a curved working face 53 of a shape adapted
the cutters are in operation thereon. This rock
to generate the desired heel curve or contour 3%?
resulting from the combined inward movement of 65 ing motion is placed under the control of a cam.
By properly shaping the cam a desired shape
the cutter and the transitional movement of the
may be imparted to the toplift end of the heel.
heel block in the cutting zone.
The heel blocks may be given this rocking
The various positions of one of the cutters 21
motion in any suitable manner. The means for
with respect to a heel block 3| and the various
positions of the cooperating earns 53 and 38 with 70 accomplishing this result as shown in the draw
ings constitutes a part of the invention. It is a
respect to the follower rolls 31, are illustrated
very important consideration in developing and
in Figs. 9, 9-—A, 9-—B and 9-—C in connection
designing a machine of the type presented here
with a cutting cycle. In‘the operation of the
with, to insure the maximum rigidity of all parts.
apparatus as shown for example in Fig. 9, the
Without
rigidity the resulting vibrations cause
75
carrier 20 moves in the direction of the arrow
2,405,941
rough unsatisfactory surfaces upon the heel.
A mechanism for tilting the heel must therefore,
be of such a nature as to maintain a ?rm and
stable grip upon the block through the shaping
operation. To accomplish the desired end the
heel block jacks is, as shown in Figs. 3 and ll, are
made in two major sections a base section 54
10
is composed of two sections which are held to
gether by screws M which clamp the two sections
upon the jaw
Screws it‘!- pass through a ver
tical slot 75 in the membertd. When the screws
are loosened the jaw member 53 may then be
raised or lowered with respect to the ram to
permit clamping heel blocks of various sizes in
the jack. When the desired adjustment has been
made the screws ii are tightened.
and a movable block clamping section 55. The
base section for structural reasons is best com
posed of three parts a central main supporting 10
The lower extremities of the ram sections are
element 56 in the form of a flat plate having
provided with lateral extension ‘5'6 against which
parallel nicely ?nished surfaces. The plate 56
projects outward from the periphery of the car
the lower end of the springs ‘H bear. The other
end of the springs seat against the end walls of
rier wheel 26 and is provided with an aperture
the apertures T2. The lower end of the ram 13
5'! (Fig. 3) within which a pivot pin 53 is received 15 has rotatably mounted therein a roll it which
upon which the block clamping member 55 rocks.
is engaged by a cam ‘it upon a cam shaft ‘i9
The plate 55 is rigidly anchored between the two
extending laterally through and having a bearing
sections 59 and $8 of the wheel 20. The two sec
in the carrier 28. The cam ‘i8 and its actuating
tions of the wheel are joined together by screws
shaft 19 act to raise the clamping jaw 68 to re~
5| which pass through apertures in the lower end
lease a processed heel and permit insertion of a
of the plates 56. The plates 56 are held in per
rough block in the jack. The operation of the
fectly true and ?xed position by means of a pair
clamp releasing mechanism will be described
of pins 52 to insure that the axis of the pins 53
hereinafter. To limitv the downward travel of
will remain in accurately spaced relation about
the ram 73 when no heel is in the jack 9. pair of
the wheel 26 and equally distant from its center. 25 bolts or screws 83 are provided. These screws
Inasmuch as all of the jacks on the carrier 2d
pass through apertures in the ram extensions 76,
are identical it is deemed su?icient to describe
project through the central apertures of the
only one. The movable section 55 of these jacks
springs and are secured by’ screw threads in the
contains the block clamping element and has
end walls of the chambers l2. Screws 8B are of
formed therein a central vertical slot 63 extend 30 the correct length to permit free movement of
ing for a portion of its length from back to front
the ram for all normal operations of the machine
and within which the plate 55 is received with
,but prevent movement beyond that which is
a close but free ?t against the sides of the plate.
necessary by reason of the engagement of the
The slot is of suflicient extent to permit the
extensions 15 with the heads of the screws. The
member 55 to freely rock within the limits of the 35 #screws ‘11i- project into a slot in the member 55
degree of motion required to produce any desired
heel shape. At the lower portion of the member
(Figs. 4 and 5) thereby permitting free move
ment of the ram ‘Hi.
Free access to the screws
55 its outer or side faces 64 are ?nished accu
is this also permitted for the purpose of adjust
rately ?at and parallel to the plate 55.
ring the position of- the jaw ea.
As above suggested the base portion 54 of the 40
It has been suggested hereinbefore that addi
jack is composed of three elements one of which
tional control of movement between the block
is the plate 55 already described. The other two
and cutter should be provided to supplement that
elements are in the form of angle plates 65 rig
induced bythe cam 5%. To produce this added
idly secured upon the periphery of the carrier 2!!
control automatic means are provided for tilting
by means of screws
(Figs. 5 and 6). The inner 45 ‘the heel blocks in timed relation to the progress
faces 87 of the angle plates 65 are machined accu
of the cutters along the blocks. Any suitable
rately ?at and placed in contact with the faces
mechanism may be employed for this purpose.
65 of the member 55. By supplying all of the
A desirable means for accomplishing the required
interengaging faces between the members 55 and
results is shown in Figs. 3 to -6 of the drawings
55 with lubricant the member 55 is readily mov 50 wherein a link and lever mechanism is provided
able but is rigidly held against all movement
\for each jack 59. Since all of these mechanisms
other than that in a true plane parallel to the
are the same, only one will be described. Of the
plane of movement of the carrier 29.
two sections 59 and 6b of the wheel 2%}, the‘ section
The heel blocks 35 are clamped in the member
59 is‘the main section and has a web 85 extend
55'by means of a clamp jaw 68 which engages 55 ing between its rim or peripheral portion and its
the toplift end of the block. The heel seat end
hub 82. The hub is rigidly keyed to its drive
of the block rests upon the jack plate t9 which,
shaft 2!.
as shown in Fig. 4, is provided with an adjustable
The section 55 of the jack which carries the
breast gauge ii] which. determines the back and
block 3| is rocked by means of an actuating lever
front position of the block in the jack. An im 60 83 fulcrumed upon a stud shaft 34 secured in the
portant feature of the jack construction is that
Web 8! of the carrier 20. The lever 83 is con
which permits the jack plate 65 to be situated
nected to the jack element 55 by means of a pair
closely adjacent to the pivot pin 58. By thus
of links 85 (Figs. 4 and 5) one end of each link
positioning the jack plate, the rocking motion
being pivoted to the lever 83 upon a pivot pin
of the block has little effect upon the shape of 65 85. The links are mounted on opposite ends of
its heel seat. However, it is possible to produce
the pin 85 anchored vin the lever 33. The other
a maximum change in the toplift end of the heel
ends of the links are received in slots 8? and
which is the desired object of the rocking motion.
pivoted upon pins 88 in the member 5a. The
Block clamping pressure is derived from a pair
lever 83 is provided with a cam roll 89 which
of springs ‘H (Fig. 6) which are received in 70 engages a cam 93 having its active face devel
chambers i2 formed in the member 55. The
oped to impart a predetermined desired motion
clamp jaw 68 extends downward into the member
to the block through the lever and the links 85.
55 and is telescopically received and clamped in
Two cams 90 are provided one of which acts to
a clamp actuating ram 23 guided to move ver
tically Within the member 55. Desirably the ram 75 rock the blocks during the cutting of one side of
the heel and the other being properly situated to
2,405,941
11
12
.
TI. The manner of operating the cam ‘I8 will be
described hereinafter. It is evident that when
actuate the rocking mechanism during the shap
ing of the other half of the heel as the carrier
20 moves through its operating cycle. The cams
block releasing pressure is applied to the roll ‘IT
a very strong tendency of the roll to give way
90 are received upon cam plates 9| which in turn
are rigidly mounted upon the periphery of a
?oating wheel 92 (Fig. 3). The wheel 92 is ro
tatably supported upon the hub 82 of the carrier
23 by means of a pair of ball bearings 93.’ The
under the cam action is set up. The elements
involved must therefore, be locked against move
ment at this time.
A desirable means for ac
complishing this end is illustrated in Figs. 4, 5
and 6 of the drawings wherein the lever 83 is
provided With a rigid tail portion E00 in the lower
end of which a roll I0? is rotatably mounted. A
circular holding cam I08 is concentrically mount
ed upon the ?oating wheel 92 in position to be
engaged by the roll IG'I. The position of the
active face of the cam is such that lever 83 and
the member 55 of the jack are held in their nor
mal static position and the application of force
upon the roll 11 by the cam ‘I8 is resisted by the
engagement of the roll I01 upon the cam I08 thus
permitting the clamp jaws 03 to be raised with
out moving the member 55.
Since the holding cam I08 need function only
during the ejecting and loading period of the
machine cycle that portion of the cam which
would engage the rolls I01 during the heel shap
wheel 92, however, is held against rotation by
means of a suitable anchoring member secured to
a ?xed element upon the machine. A convenient
means for securing the wheel 92 is to provide an
anchoring member 94 rigidly fastened to the
wheel at one end and projecting laterally out“
ward therefrom and secured at its other end to
a casing or chip guard 95 which in turn is secured
to the machine frame. To provide for accurate
positioning of the wheel a short arcuate slot 96
is formed in the casing 95. A bolt 91 projecting
from the anchor member 94 extends through the
slot 96 and acts to lock the wheel in its correct
angular position after it has been timed to cause
proper synchronization of the rocking movement
of the block with the action of the cutter head.
Any other suitable arrangement for providing
this adjustment may be utilized.
ing operation is cut away to permit free rocking
movement of the heel block holding members 55
Means are provided for applying a resilient
which are at that time under the control of the
torque force to the lever 83 tending to rotate it
cam 90. Directly after the roll 89 has reached
in a. clockwise direction as viewed in Fig. 4. This
torque normally causes the clamping element 55 30 the peak of the cam 90 the spring I04 acts to
return the member 55 to its initial position. The
of the jacks to swing about its pivot 58 until the
two extremes of position of the member 55 are
clamp jaw lift roll 11 engages the cam ‘I3 where
shown in Fig. 4. On the left it is shown in its
it is held at all times until the roll 89 engages the
position of maximum displacement at the com
cams 90 during the heel shaping operation. Any
pletion of the cutting operation While on the right
suitable means may be provided for applying the
required torque to the lever 83. As shown herein
in Fig. 5 the stud shaft 84 is rigidly anchored in
the web BI by means of a nut 98 which draws a
shoulder upon the shaft ?rmly againstthe web.
The shaft 84 is provided with an axial bore as
within which a torque shaft I00 is rotatably re
ceived. The shaft I00 is provided with a head
IGI of substantially enlarged diameter. A pair
of driving pins I02 project inward from the head
40
it is shown in its initial or neutral position.
Upon completion of the shaping of the heel the
clamp jaw 68 is raised and held in raised position
for su?iciently long a period of time to permit a
processed heel to fall out and to permit the op
erator to insert a rough block. To accomplish
this result the cam shaft 79 as shown in Figs. 6,
'7 and 8 is extended outward beyond its bearings
I09 and has secured thereon at one end an op
and are received in apertures in the hub of the 45 erating arm I Ii) and at its other end an operating
arm Hi. A cam roll H2 is rotatably mounted
lever 03. The other end of the shaft I00 projects
upon the outer end of the arm III. The roll H2
beyond the end of the stud shaft 84 and has
projects into the groove of a cam H3. The cam
?xedly secured thereto an arm I03. Upon the
groove is concentric with the axis of the wheel
outer end of the arm I03 is secured one end of a
tension spring I04 (Figs. 3 and 4), the other end 50 'for a substantial portion of its length and is de
signed to manipulate the cam ‘I8 by means of the
of which is anchored upon a pin I05 ?xed in the
arm H I. The cam H3 is ?xed rigidly to the ma
wheel web 8|. The tendency therefore, is to
chine frame in any suitable manner as by so»
rotate the lever at all times and the torque de
curing it to a supporting member H4 which in
ment with the cams 90 during the shaping 55 turn is fastened to the bearing housing of the
shaft 2| by means of screws 1 I5. The position
operation.
of the cam is so adjusted that the cam roll II?!
It should be noted in connection with rocking
will engage the angular face IIB thereof at posi
the block as above described that such action is
tion A at which time the shaft ‘I9 and the cam 1'8
more e?icient than attempting to rock the cutter
head to produce the same result for a very basic 60 are rotated in a counter-clockwise direction as
viewed in Fig. 8. When the roll II2 reaches the
physical reason. A motor armature and spindle
righ point of the face H6 the arm will then be
of considerable weight when rotated rapidly offer
disposed substantially radially from the axis of
a very substantial resistance to a change in their
the shaft 2! and the roll will next engage the
axial position due to the gyratory action of the
section II‘! of the cam which will continue to
rapidly rotating elements. Such resistance to a
rotate the arm III until it assumes the position
change in axial position would interfere with the
shown at B at which time the high point of the
action of a mechanism tending to produce such
cam ‘I8 will have lifted the clamp jaw 68. This
a change. A practical mechanism for so moving
position of the parts will persist until the arm
the cutter would be extremely dif?cult to produce
reaches the position C where its control is taken
and its operation would be impractical.
70
over by another and shorter cam ! I8 (Figs. 6 and
As above stated automatic means are provided
7) . During the cycle of the machine represented
for releasing heel blocks from their jacks by lift
by the travel of the arm I I I from the B to the C
ing the jaws 68 against the clamping pressure of
position a processed heel drops out and the op
the springs ‘II and that this action is accom-,
plished by the cam ‘I8 which engages the rolls 75 erator inserts a rough blocks in the jack. To
veloped maintains the roll 89 ?rmly in engage
13
2,405,941
permit access to the jacks an opening I I9 is
formed in the casing 95 as shown
Fig. i. The
tion
casing
of .95
theiscarrier
designed
20 bearing
to cover the
a substantial
jacks I9 which
are in motion during the operation of the ma
chine and which would subject the operator to
the liability of injury from contact therewith.
A roll I29 rotatably mounted on the outer end
of the arm H9 is at this time, as shown in Figs.
6 and '7. about to enter the groove of the cam I I8.
The arm I ill is so positioned upon the cam shaft
79 at this time that it assumes a position in ad
vance of a radial line from the wheel axis and as
its roll I20 enters the groove in the cam H8 it
will engage the incline surface I2! of the cam
which causes the arm I It to rotate ina clockwise
direction. Such movement of the arm I II! results
in releasing the clamp jaw which then. engages
the unprocessed heel block placed therein by the
14
Or the other of the two elements and a pointer
on the remaining element permits accurate
recording of the adjustment. . Once this adjust
ment has been made it will be only at rare inter
vals in the operation of the machine that a
change will be required.
-
‘
The third member I35 of the bracket 29 has
vertical movement upon the member I218. The
motor 28 having the cutter 2‘? upon its spindle
is securely ?xed upon the member @355. Vertical
movement of the member. I35 raises or lowers the
cutter 27 thereby to adjust its vertical position
with respect to the heel block 3i. This adjust
ment may be necessary to establish cutting rela
tion with the block at a predetermined portion
of the blades of the cutter. This vertical adjust
ment is provided for by a dovetail slide connec
tion {365. To simplify the vertical adjustment of
the cuttera hand wheel i3? is provided secured
operator. The action or" the cam lit. and the 20 to a vertical shaft I 38 having a bearing in and
arm I I0 is shown graphically in Fig. 7 wherein
held from axial movement within a bracket I38
the roll 12!) is shown entering the cam groove in
mounted rigidly upon the member I241. The
full lines and in dotted lines the positions are
lower end of the shaft 538 has screw'threaded
shown which it assumes as it traverses the cam.
When the arm l I0 has reached the position shown
by the left hand dotted position the arm II I and
the roll H2 will be received in the groove of the
cam H3. During the above series of operations
the groove in the cam I i3 is discontinued to per
mit the cam I I8 to function. The roll H2 will
then continue to traverse the concentric portion
of the cam H3 until it again reaches the angular
face II 6 thereof from where the action is re
peated.
To set up and adjust the machine to produce a ‘
speci?c heel, it is found desirable to provide for
adjusting the cutter heads 2'! into predetermined
precise relationship with respect to the blocks 3| .
To provide for this adjustment. the motor bracket
as shown in Figs. 11 and 12 is divided into three
sections, a main supporting plate I22 having a
pair of bosses 523 (Fig. 1) through which the.
shaft 32 passes and to which it is rigidly secured.
An intermediate bracket member I2"; is pivotally
secured to the outer fiat face of the supporting
plate I22. The member I21! pivots upon a stud
screw E25 rigidly secured in the plate I221. The
screw is situated at the lower portion of the mem~
engagement with the member I 35. ‘ Rotation of
the hand wheel I3? raises 0r lowers the motor
and cutter. After correct adjustment has been
_ made the two elements I24 and I35 are locked to
gether by means of a screw I453 having threaded
engagement with the member 935 and passing
through a vertical slot IdI in the member I24. To
look the members the screw is rotated by means
of a handle Hi2. Desirably a scale I43 is provided
upon one of the two members having a cooperat
ing indicator upon the other by means of which
the position of the cutters may be recorded for
future reference. Other suitable means may be
employed for effecting the adjustment of the cut
ters. The means shown and described is only one
desirable construction.
To produce heels of different sizes the cutter
blades 544 (Fig. 11) in the’ cutter head 21 are
adjusted to effect the desired size change in the
manner customarily employed in the heel turn
ing art. Another desirable adjustment is provided
‘by means of which the contour and dimensions
of the toplift end of the heel may be controlled.
To accomplish this result the cams 9e’! are ar
ranged in a manner to enable their effective con
her I 24 substantially on a level with the cutter 21.
tour to be changed in accordance with the de
The upper edge of the member i2=l has teeth 50 ‘sired results.
A desirablev construction for exe»
formed therein to constitute a
segment I26
outing this adjustment is shown best in Fig. 4.
on a radius the axis of which lies upon. ‘the axis
The cams 98' are arranged to provide for raising
of the screw $25. The upper end of the member
or lowering the high end of the cams without
I24 is held firmly against the member I22 and
substantially changing the effective height of
guided in its movement by a retaining member
their other end. It is unnecessary to provide
I 2? having the general contour of the toothed
special adjusting means to modify the curve along
segment. The member I2? is securely fastened to
no side portions of the toplift end of the heel
the plate I22 by screws I28 and is provided with
apart from the ordinarily provided means- for
a, flange which overlies the member 524 and re
initially setting up the machine to produce a
tains the two members in face to face contact. 60 given style. Once the style of this portion of the
To provide a readily operated means for obtain
heel is established by the general contours of the
ing accurate angular adjustment of the cutter
cam: and by the position Of the cutter blades with
heads a worm I29 is provided which meshes with
in the cutter head 21 it is unnecessary to make
the segment I26. The worm I29 is secured upon
a further adjustment at the side portions of the
the end of a shaft I39 rotatably mounted in the 65 heel. However, it is desirable to have available
member I21. The shaft I39 projects outward
a means for adjusting the curve along the back
from the member !2i and is provided with a
of- the toplift end since, in changing from size
square end I3I upon which an operating handle
to size an undesirable distortion will in some cases
or wrench not shown may be placed. To make
at this portion of' the heel. This distor
the desired adjustment the worm is rotated until 70 tion may ‘be ‘corrected by a slight rise or drop
the correct angle is obtained at which time a pair
at the high end of the cam‘. This adjustment
of bolts I32 are tightened to lock the two elements
also provides a valuable means for establishing
I22 and I24 together. To provide for this ad
the correct slope of the cam at the time of the
justment the shanks of the bolts I32 pass through
initial adjustment of the machine to insure pre- Y‘
slots I 33 in the member I22. A scale I34 on one 75
cise coordination of the movement of the ele
2,405,941
15
ments of the machine as created by the cams 50
and 90. Any suitable means may be provided
for adjusting the pitch of the cams 90. As here
in. shown the cam is pivotally supported at its
low end to the cam plate 9| upon a pivot screw
M6. The other end of the cam is provided with
a stud I41 rigidly anchored in. the cam and pro
jecting through and beyond the outer face of
the plate SI. A pair of adjusting screws M'I are
16
style requires a different pro?le curve new cutter
blades are installed in the cutter heads bearing
the required contour, or the cutter heads are
vertically adjusted to present a different portion
of their cutting edge to the blocks.
I claim:
'
l. A heel shaping apparatus comprising a sup
porting frame, means on said frame for holding
and translationally feeding heel blocks through
provided which engage the stud I41 respectively 10 a cutting zone at constant and uniform speed
while con?ning the motion thereof to a single
from its top and bottom extremities. The screws
plane, a heel shaping tool, means for swinging
I48 are supported by and have screw threaded
said tool inward into cutting relation with the
engagement in a pair of posts I49 rigidly ?xed
said'blocks; pattern means for controlling and
in the cam plate 9|. Fine angular adjustment
of the cam 90 is thus provided by rotating the 15 co-relating said inward swinging motion with said
translational motion of the blocks to produce a
screws I48 and when the exact position desired
is determined a ?nal turn of one screw will lock
predetermined heel shape, the inward path of
travel of said tool having a predetermined course
calculated to provide a predetermined speed of
the cam 90 upon the plate 9I a locking screw I50
is provided which passes through a vertical slot 20 travel of the tool along the heel at the cutting
line, and means to rock the heel block a limited
I5I in the plate and has threaded engagement
amount in a plane substantially parallel to the
with the cam. Tightening the screw I50 causes
heightwise axis of the heel being produced and
its head to ?rmly engage plate 9| and lock it to
to the plane of its path of travel further to con
the cam 95.
‘
'
To assist the operator to execute the initial 25 trol the heel shape.
2. A heel shaping machine comprising a sup
adjustments on the machine a further desirable
porting
frame, a conveyor movable upon the
adjustment is provided which is shown in Fig. 9
frame, at least one heel block holding jack on
wherein the shape cam 50 may be moved toward
said conveyor operable to receive and carry a
or from the carrier wheel 20. The cam 50 has
heel block through a cutting zone, a heel shaping
formed therein a groove I52 extending substan
tool, a tool supporting arm pivoted upon said
tially perpendicular to the plane 34 of the carrier
frame operable to move said tool into cutting
29 within which a boss I53 formed upon the arm
relation with saidheel block, a cam connected
39 is received. The boss ?ts the groove snugly
to said arm, a follower on said conveyor for each
and the two elements are held in desired 'ad
the parts in adjusted position. To rigidly secure
justed position by a, clamp screw I54 the shank 35 jack against which said cam is held during the
of which passes through a slot I55 in the cam.
Adjustment in or out of the cam 50 can be made
to effect the desired machine operation and the
correct cam setting may be recorded by noting
its position as indicated on the scale I56.
While the operation of the device will be ap
shaping operation acting to control the swinging
movement of the cutter to co-relate such move
ment with the feeding motion of said conveyor
to produce a predetermined heel shape and means
40 acting to rock said jack with respect to said con
veyor under the control of a pattern means there
by further to control the shape of the heel.
parent from its disclosure in connection with the
3. A heel shaping apparatus comprising a sup
above vdescription, it may be of advantage to
porting
frame, a driven conveyor movable upon
briefly restate the main operational features in
their normal sequence. The operator is given a 45 said frame, a plurality of heel block holding jacks
secured to said conveyor having movable block
model heel hearing all the required character
clamping elements, a heel shaping tool, a sup
istics of the heels to be produced upon the ma
porting arm for said tool pivoted upon said frame
chine. Along with this model heel the operator
operable to swing the tool in a plane substan
is provided with the necessary number of cams
59 and 90 hearing the required curvature upon 50 tially at right angles to the heightwise axis of
the heel being produced and into cutting rela
their active faces to produce the desired contours
tion with the blocks carried by the jacks, means
upon ‘the heel. The cams are ?tted into place
to coordinate the movement of the tool and the
and the cutter heads, which have been supplied
movement of the blocks to produce a predeter
with blades bearing the required pro?le, are ad
mined heel shape, automatic means for rocking
55
justed into correct position with respect to the
the said heel block clamping elements with re
blocks. The machine is then ready to start upon
spect to the jacks in a plane parallel to the height
a production run. After starting it the operator
wise axis of the heel and in timed relation to the
stands before the machine and places heel blocks
movement of said tool, said automatic means
into the heel jacks as they are successively moved
into the loading station B by the constantly driv 60 including a cam ?xed with respect to said frame
and a follower for each jack engaged by said cam
en carrier wheel 20. Just prior to the loading
acting to rock said block clamping elements dur
operation, the clamping jaw 68 of each jack is
ing the heel shaping operation thereby to intro
automatically raised at which time a processed
duce an additional controlling factor to vary the
heel drops out of the jack after which the oper
heel
shape.
65
ator inserts an unprocessed block by placing it
4. An automatic heel shaping apparatus com
upon the jack plate 69 with its breast face en
prising a frame, a conveyor supported by and
gaging the breast gauge ‘I0’ and in a position
movable
upon said frame, means for driving said
laterally central of the jack. The clamp jaw 68
conveyor
at uniform speed to feed h'eel blocks to
then descends and the block passes into the ?rst
cutting zone where one side of the heel is formed 70 and through a heel shaping Zone, a rotary heel
shaping tool, a tool supporting arm pivoted at one
in the manner above described after which the
of its ends on said frame upon an axis substan
?nal out is made upon the other side of the block
tially parallel to the heightwise axis of the heel
by the second cutter blade 21. Adjustments are
being produced and having said tool mounted
made for different size heels in the same style
in the manner above described and when a new 75 upon its other end, said arm acting to move said
17
2,405,941
tool into heel sh‘aping relation to the heel blocks,
the axis of said pivot and said tool lying upon
a plane extending outward away from said con
veyor at an angle between 30° and 60° with re
spect to the plane of travel of the said height
wise heel axis, and means for co-relating the
movement of said arm with the translational
movement of the blocks during the shaping op
erations thereby to produce a predetermined h'eel
18
cutter arm during the cutting operation thereby
to produce the desired heel contour, the pivot 01’
said arm being situated substantially to one side
of the line of movement of the heel blocks.
' 8. A heel shaping apparatus comprising a
shape.
frame, a circular heel carrier rotatably mounted
upon the frame, a plurality of heel block holding
jacks mounted upon the periphery of said carrier
having means to receive and feed rough h'eel
5. An automatic heel shaping apparatus com
prising a frame, a conveyor movably mounted
blocks to and through a cutting Zone, a cutter
supporting arm pivoted ‘upon said frame upon
an axis substantially parallel to the heightwise
on said frame, means for driving said conveyor I
axis of the heels being produced at said cutting
at a uniform speed, a plurality of heel block hold
ing jacks mounted upon said conveyor, a driven 15 zone and situated upon a plane extending out
ward from said cutting zone at an acute angle to
rotary heel shaping tool, a tool supporting arm
the
plane of the path of travel of the said height
pivoted at one of its ends on said frame upon
wise axis of the heels a driven heel shaping cutter
an axis substantially parallel to the heightwise
rotatably mounted upon the outer end of said
axis of the heels being produced and having said
arm,
pattern means for controlling the swinging
tool mounted upon its outer end, said arm acting 20 movement
of said arm during the cutting opera
to move said tool into heel shaping relation with
tion to produce the desired heel shape, a second
said heel blocks as they are fed into shaping po
pattern means acting in timed relation to the ac
sition by said conveyor, the axis of said pivot and
tion of the cutter to rock the heel blocks "with
said tool lying upon a plane extending outwardly
respect to said carrier in a, plane parallel to the
from said conveyor at an angle between 30° and
plane of travel of the blocks during the heel sh'ap
60° with respect to the plane of travel of the said
ing
operation thereby further to control the heel
heightwise heel axis, a pattern cam ?xed to said
shape.
arm and a follower for each of said jacks mount
9. An automatic heel shaping apparatus com
ed upon the carrier co-acting with said pattern
prisinga
frame, a conveyor for holding and feed
cam. to co-relate the swinging of said arm with‘ 30 ing rough heel blocks into and through a cut
the translational movement of the blocks during
ting zone, a power driven rotary h'eel shaping
the shaping operation thereby to produce a pre
tool, a supporting arm upon which said tool is
determined heel shape.
mounted pivoted upon said frame at one side of
. 6. An automatic heel shaping apparatus com
said conveyor and'operable to swing said tool into
prising a supporting frame, a conveyor mounted
working relation with said blocks at said cutting
on the frame, a plurality of heel block holding
zone, pattern means for coordinating the move
jacks on said conveyor, block clamping means on
ment
of the cutter with the feeding movement of
said jacks operable to rock the jacks in a plane
the blocks to produce the required heel shape,
parallel with the plane in which the heightwise
and weighted means connected to said arm act
axis of the heels being produced travel, a rotary 40 ing
to move the arm into its working position
heel shaping tool, a tool supporting arm pivoted
during the heel shaping operation.
at one of its ends upon said frame upon an axis
10. An automatic heel shaping apparatus com
parallel to the heightwise axis of the heels being
prising
the elements de?ned in claim 9 together
produced, said arm having a cutter mounted at
with a pattern cam on said arm, and a follower
its outer end whereby said tool may be swung into \
connected to said conveyor co-actingwith said
active engagement with the heel blocks as they
cam to cause the movement of the arm to ‘pro
are fed into the heel shaping zone, the axis of said
duce the desired'heel shape.
arm and of said tool lying upon a plane extends
11. An automatic heel shaping apparatus com
ing outward away from said conveyor at an angle
between 30° and 60° with respect to the said 60 prising a frame, a circular conveyor rotatably
mounted on said frame, a plurality of heel block
plane of travel of the heightwise heel axis, pat
holding jacks mounted upon the periphery of
tern means for co-relating the swing of said arm
said conveyor, a block clamping member for each
with the translational movement of the blocks
jack pivoted to rock in an are parallel to the
during the shaping operation, and means col-act
of movement of the jacks, a lever for each
ing with said pattern means for simultaneously 55 plane
clamping member pivoted on said conveyor and
rocking said block clamping means thereby‘ to
produce a predetermined heel shape.
7. An automatic heel turning apparatus com
prising a frame, a conveyor movable ‘upon said
operably connected to the said block clamping
means to rock them upon movement of the lever,
a cam ?xed with respect tosaid frame acting to
engage said lovers to rock said clamping mem
frame, means for driving said conveyor continu
bers during the heel shaping operation, a pair of
ously and at uniform speed, a plurality of heel 60 driven
heel shaping cutters situated upon oppo
block holding jacks on said conveyor, each of
site sides of said conveyor acting to shape the
said jacks including a pivoted block-clamping
opposite sides and back portions of the heel, a
element, a heel shaping cutter, a cutter support
supporting arm for each‘ cutter pivoted upon said
ing arm pivoted at one of its ends upon said
frame and operable to swing the cutters into cut
frame upon an axis substantially parallel to the
ting position and pattern means acting together
heightwise axis of the heel being produced‘ and
with said block rockingmeans to produce a pre
having said cutter rotatably mounted upon its
determined heel shape.
outer end, said arm acting to move said cutter
12. An automatic heel shaping apparatus com
into cutting relation with heel blocks carried by
said jacks, controlling means for rocking said 70 prising the elements contained in claim 11 to
gether with means for guiding said cutter to move
block-clamping elements in timed relation to the
in a path in a direction extending at an acute
progress of the cutter along the heel blocks and
angle to the plane of travel of the heel blocks
in the plane of the bodily travel thereof, and pat
tern means for controlling the movement of the 75 and substantially at right angles to the height
wise heel axis during the cutting operation.
2,405,941
19
' 13. An automatic heel shaping apparatus com
prising a frame, a circular conveyor member ro
tatably mounted on said frame, a plurality of
heel block holding jacks mounted On said con
veyor said jacks having two major elements, a
fixed: element secured to the carrier and a block
clamping element, means for pivoting said clamp
ing element upon said ?xed element to swing in
a plane parallel to the plane of bodily travel of
20
and automatic means acting to release a shaped
heel from said clamps and permit an un?nished
heel block to be inserted therein.
16. An automatic heel shaping apparatus com
prising a frame, a circular carrier rotatably
mounted on said frame, power means for rotat
ing said carrier including a rigid drive shaft upon
one end of which said carrier is secured, a plu
rality of heel block holding jacks mounted on
said jacks, relatively large flat inter-engaging 10 the periphery of said carrier, each jack having a
block clamp pivoted to swing in a plane parallel
areas upon said ?xed element and said clamping
to the plane of the carrier, a pair of driven cut
element rigidly to guide the clamping element in
ters for shaping the heel, a supporting arm for
its rocking movement, means on said conveyor
each cutter pivoted upon said frame upon oppo
for swinging said block-clamping element on its
site sides of said carrier, cam pattern means act
pivot in a plane parallel with said flat areas,
ing to control the movements of said arms to
power driven cutting means for shaping heels
shape opposite sides and back portions of the heel
from said blocks, and pattern means for ,coordi
to the desired shape, a cam supporting bearing
nating the movement of said cutters with the
axially mounted upon the hub of said carrier and
swinging movement of said clamping element
a connection between said cam supporting bear
thereby automatically to form the desired heel
ing and said frame whereby said cam supporting
shape.
,
.
. 14. An automatic heel shaping apparatus com
prising a frame, a carrier rotatably mounted on
said frame, power means to rotate said carrier,
bearing is held against rotation while permitting
said carrier to rotate, a lever for each of said
jacks mounted upon said carrier and having a
operable to rock its respective block
a plurality of heel block holding jacks mounted 25 connection
clamps, cams ?xed on said cam supporting hear
upon the periphery of said carrier each of said
ing engaged by said levers acting to rock the
jacks having a block clamping member pivoted
block clamps during the heel forming operation,
to swing in a plane parallel to the radial plane
a holding cam on said cam support bearing act
of said carrier said carrieracting to feed the heel
ing through said levers to lock said block clamps
blocks continuously and at uniform speed during
in their starting position and to release them
the heel shaping operation, a pair of power driven
during the cutting operation, said block clamp
heel shaping cutters, a" pair of supporting arms
releasing means including an operating lever for
for said cutters arranged on opposite sides of said
each block clamp, and an annular cam generally
carrier and pivotally mounted on said frame op
concentric with the axis of said carrier and ?xed
erable to move said cutters into heel shaping po
to said frame acting through said cam releasing
sition, cam means for controllinglthe movements
means to release the ?nished heel and permit
of said arms during the heel shaping operation
insertion of a roughblock in said clamping mem
to - produce a desired heel shape, :block clamp
manipulating means including a lever'for each
ber.
15. An automatic heel shaping‘apparatus com
prising a frame, a carrier movably mounted upon
said frame, power means to move said carrier at
cam to release the jaw into clamping position
a block clamping member pivoted to swing in a
plane extending in the direction of movement of
said jacks,v a pair of power driven heel shaping
tools,;a pair'of supporting arms upon which said
tools are mounted said arms being situated upon
opposite sides of said carrier pivoted upon said
frame and operable to move said tools into heel
forming relation with the heel blocks carried by
speed, a plurality of heel block holding jacks on
said conveyor each jack having a block clamping
element pivoted to swing in a plane in the direc
17. An automatic heel shaping apparatus hav~
jack'pivotally mounted on said carrier and having 40 ing the elements defined in claim 16 together
a connection acting to rock said’ block clamps
with means for operating said block clamping
upon movement of the lever, a pattern cam ?xed
means to permit it to grip and hold the block
with respect to said frame and engaged by said
during the heel shaping operation including an
levers acting to rock said block clamp during
auxiliary cam on said cam support bearing, a
the heel shaping operation thereby further to
clamping jaw for engaging the heel block, and
control the shape of the heel.‘
'
jaw operating means engaged by said auxiliary
prior to the heel forming operation.
18. An automaticheel shaping machine com
uniformlspeed, a plurality of heel block holding 50 prising a frame,-a conveyor movable upon'the
jacks mounted upon the carrier each jack having
frame, means to move the conveyor at a uniform
the carrier, cam means for controlling the move
ments of said arms during the heel forming op
tion of movement of the jacks, a pair of power
driven heel shaping tools, a supporting arm' for
each tool pivoted on said frame upon opposite
sides of said conveyor operable to move said tools
into cutting position with respect to the heel
60 blocks to form respectively the opposite sides and
back portion of the heel, pattern means acting
eration to produce the desired heel shape, one
during the cutting operation for controlling the
of said tools acting to form one side of the heel
movement of said arm to cause said tools to pro
and the other tool acting to form the opposite
duce a heel of the desired shape, a control lever
side of the heel, block clamp manipulating means G5) {01' each jack pivoted upon said carrier, a posi
including a lever for each jack pivotally mounted
tive connection between said, levers and said block
upon said conveyor and having a connection op
clamps acting to transmit motion of 'said levers
erable to rock said block clamp upon movement
tosaid clamps, pattern cams acting to engage
of said lever, a pattern cam ?xed with respect to
said levers during the cutting operation and to
said frame and engaged by said levers which act
rock the’heel block clamps during the heel shap
to rock-said block clamps during the heel shap
ingoperation thereby further to control the shape
ing operation further to control the heel shape,
of .the heel,‘ spring, means acting yieldingly to
means acting through said levers to lock said
maintain engagement between said levers and
block clamps in their starting position and re
lease‘ them , during the heel‘ shaping _ operation,’ 7.5 said cams, ,a clamping law on saidblock clamps
2,405,941.
21‘
22
-
having springs urging the jaw into clamping re
lation with said blocks, J'aw lifting means for
lineof the heel as the heel block advances through
the cutting zone, the improvement‘which' co'm-'
prises means for mounting said cutters on said"
each jack having an actuating lever, cam means
for engaging said jaw lifting lever acting upon
frame with one cutter on each side of said con
veyor, and means for moving each cutter 1n' the
direction of movement of the heel block- as the
cutter moves around the back portion of the
completion of the heel shaping operation to re
lease the completed heel, and a holding cam
?xed with respect to said frame acting to- engage
and lock said control levers against movement
heel block.
thereby to hold said block clamps against rocking
23. In an automatic heel-turning machine, a‘
movement during the lifting of said clamp jaws. 10 frame,
a conveyer movable upon said frame,
19. An automatic heel shaping apparatus com
means for driving said conveyer at a’ uniform
prising a frame, a conveyor on said frame, means
speed, a plurality of jacks on said conveyer for
for driving said conveyor, a plurality of heel block . holding heel blocks to be out, a h'eel-shapingcut
holding jacks mounted on said conveyor, each
ter supported on an arm having one end pivoted
jack including block-clamping members for re 15 upon said frame upon an axis substantially par
ceiving and holding h‘eel blocks during the shap
allel to the heightwise axis of the heel being out’
ing operation, pivot pins for pivotally supporting
said block clamping members, said pins being
situated below and closely adjacent to the seat»
of the heels being produced and disposed to per
by the cutter, said cutter being rotatably mounted
upon the end of said arm opposite its pivot, said
arm being adapted to swing said cutter into cut
20
mit swinging said clamping members in a'plane
extending in the direction of motion of said jacks,
a pair of driven heel shaping tools situated upon
opposite sides of said conveyor, means for moving
said tools into cutting relation with the blocks to
a direction opposite to that of the movement of
the jacks, whereby said cutter may be advanced‘
in the direction of movement of the jacks during
the cutting of the back portion ,of theheel blocks.
24. In an automatic apparatus for shaping
perform the heel shaping operation, cam pattern
means acting, to rock said block clamping mem
bers about said pivot pins during the heel shaping
operation further to control the heel shape.
20. A heel-shaping apparatus, comprising a ~
frame, means for holding and feeding heel blocks
through a cutting zone in a path con?ned to a
plane and at a constant and uniform speed, a
tool mounted on said frame for shaping the heel
blocks, means for swinging the tool into cutting ‘
relation with the heel blocks as they pass through
the cutting zone, pattern means mounted in ?xed
relation to said tool and adapted to be swung
therewith, said pattern means acting to correlate
the inward swinging motion of the tool toward
the blocks in the cutting zone with the transi
tional motion of the heel blocks to produce a
predetermined h'eel shape, and means cooperat
ing with said swinging means for advancing the
tool in the direction of movement of the block
being cut in the cutting zone during the cutting
of the back portion of the heel block.
21. A heel-shaping machine, comprising a sup
porting frame work, a conveyer movable upon
said frame work, at least one jack on said con
veyer for holding a heel block, said conveyer be
ing arranged to advance said jack and a heel
block h‘eld therein in a, plane through a cutting
ting relation with heel blocks ‘carried by said
jacks, the pivot of said arm being situated sub
stantially to one side of the line of movement of
said jacks, and said arm normally extending in
heels, a frame, a conveyer on the frame having
clamping means for holding a plurality of heel
blocks in spaced relation, means for driving said’
conveyer to move said blocks at a uniform speed,
a cutter for shaping said heel blocks mounted
on a supporting arm pivoted to the frame upon 'an5
axis which is substantially parallel to the height
wise axis of the heel blocks at the cutting posi
tion, said arm extending generally alongside said
conveyer from said pivot point in a direction 0D
posite to the direction of movement of said heel
blocks, said cutter being arranged to shape one
side of each heel from the breast corner to the
back line of the heel as the heel is moved by the
conveyer relative to the pivot point of the arm,
the pivot axis of said arm being situated a sub
stantial distance to one side of the conveyer and
from the line of movement of the heel blocks but
less than the length of the arm supporting the
cutter, whereby the cutter in moving around the
back portion of the heel is adapted to move for
50 ward with the heel block and thereby increase
the time available for cutting the back portion
of the heel to the back line thereof.
25. In an apparatus for automatically shaping
zone at a constant and uniform speed, a heel
-heels, a frame, a conveyor on said frame for
shaping tool supported on an arm pivoted upon 55
supporting and advancing heel blocks in a given
said frame forward of the cutting zone and sub
direction through a shaping zone, a rotary heel
stantially to one side of said plane, said arm be
shaping tool mounted on one end of an arm
ing arranged to swing in a, plane substantially at
having its other end pivoted to the frame at one
right angles to the plane of travel of said jack
side of the conveyor and forward of vsaid shaping
and to move said tool into cutting relation with
zone in the direction of movement of the con
the heel block in said cutting zone, a cam con 60 veyor, said arm being adapted to swing said tool
nected to said arm, a follower on said conveyer
into heel-shaping relation to the heel blocks as
for each jack against which said cam is held
they are advanced through said zone, the angle
during the heel-shaping operation, said cam act
between said arm and the plane of movement
ing to correlate the swinging movement'of the 65 of the heel blocks through the cutting zone being
between 30° and 60°.
of the heel block through the cutting zone to
26. In an apparatus for automatically shaping
arm and of the tool thereon with the movement
generate a predetermined heel shape upon one
half of the heel block.
22. In an apparatus for shaping h'eels, includ
ing a frame, a conveyer for supporting and ad
vancing heel blocks in succession through a cut
heels, a frame, a conveyor on said frame for
supporting and advancing heel blocks in a given
70 direction through a shaping zone, a rotary heel
shaping tool mounted on one end of an arm
having its other end pivoted to the frame at one
ting zone in a predetermined path, and a pair of
side of the conveyor and forward of said shaping
cutters arranged to successively out each block
in the direction of movement of the con
on its respective sides from the breast to the back 76 zone
veyor, said arm being adapted to swing said tool
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