Improvements in Pegging Machines for Boots and Shoes.
Year: 1897

page_text: Date of Application, 17th Apr., 1897-Accepted, 3rd July, 1897
[Communicated from abroad by DAVEY PEGGING MACHINE COMPANY of 105
Bedford Street, Baston, Massachusetts United States of America,
Manufacturers.]
Improvements in Pegging Machines for Boots and Shoes.
I, HENRY HARRIS LAKE, of the firm of HASELTINE, LAKE & Co., 45 Southampton
Buildings, in the County of Middlesex, do hereby declare the nature of this inven-
tion and in what manner the same is to be performed, to be particularly described
and ascertained in and by the following statement:
This invention relates to a pegging machine for pegging boots and shoes and
is shown as embodied in a machine for pegging on a horn after the last is drawn
from the boot or shoe to be pegged, although portions of the invention are applic-
able to machines for pegging a boot or shoe while on the last.
In the machine herein shown embodying this invention, means are provided for.
cutting off the projecting ends of the pegs inside the sole, as the said pegs are
driven, and the invention consists in part in novel features of construction and
arrangement of the horn tip or work support and connecting mechanism therein,
whereby the cutting operation is performed neatly and efficiently, and the inven-
tion further consists in novel feed mechanism for feeding the stock, and in the
combination thereof with said work support.
The invention further consists in a stock gauge of novel construction and in
novel features of construction of the main frame work or support of the machine
in conjunction with suitable construction of the working parts thereof whereby
the head or working portion of the machine may be set at different heights or
adjusted to the convenience of any given operator.
The invention further consists in various details of construction that will be
hereinafter pointed out.
The machine herein shown as illustrating the invention is adapted for operating
with wooden pegs, and is herein so described, but it is obvious that the invention
or portions thereof are equally applicable to machines for operating with fasten-
ings of metal or other suitable material, and the invention is therefore not limited
to a machine for operating with wooden pegs, and the term "peg" is intended to
include any fastening capable of being operated upon by the instrumentalities
hereinafter described or any of them, and the term "pegging machine" is intended
to include a machine for operating upon any kind of fastening that can be used
in connection with the essential operative elements of the machine.
Figure 1 is a side elevation of the head or upper portion of the machine com-
prising the main shaft and main operative mechanism for feeding the stock and
driving the pegs;
Figure 2 a sectional detail thereof on line
;
Fig. 3 a side elevation partly in section of the base or stand of the machine,
and the horn or work support;
Figure 4 a cross section on line x of Figure 3:
Figure 5 a front elevation of the head of the machine showing also the upper
portion of the horn and supporting columu ;

page_text: Figure 6 a longitudinal sectional plan of the head of the machine;
Figure 7 a longitudinal sectional detail showing the clutch and stop mechanism;
Figure 8 an end elevation of a portion thereof;
Figure 9 a detail showing portions of said clutch and stop mechanism detached;
Figure 10 a detail showing in perspective portions of the awl operating and
feeding mechanism;
Figure 11 a sectional detail of the carrier for the awl and driver bars showing
the feed and driver bar actuating cam in front elevation ;
Figure 12 a sectional elevation of a portion of the devices shown in Figure 10;
Figure 13 a front elevation of the horn support, and mechanism co-operating
with the horn;
Figure 14 a central longitudinal section thereof on a plane on right angles 'to
the plane of elevation of Figure 13;
Figure 15 a longitudinal section of the horn showing a portion of the cutter
actuating mechanism therein;
Figure 16 a horizontal sectional plan on line 16 of Figure 15;
Figure 17 a plan of the horn tip or work support;
Figure 18 an elevation showing the lower side of the horn tip;
Figure 19 a longitudinal section thereof;
Figure 20 a transverse section thereof on line 20 of Figure 19;
Figures 21 and 22 a longitudinal section, and an elevation showing the lower
side of the horn tip, and a modified construction of the cutter mechanism therein;
Figure 23 a sectional plan on line 2, Figure 1, showing the peg wood feeding
mechanism;
Figure 24 a rear elevation of a portion thereof;
Figure 25 a horizontal section on line 2, Figure 24;
Figure 26 a plan of the edge gauge for the stock;
Figure 27 a front elevation thereof;
Figure 28 a side elevation thereof; and
Figure 29 a sectional plan on line 29 Figure 28.
The main frame work A of the head portion of the machine containing the awl
and driver and actuating mechanism therefor is supported on the upper end of a
two-part column or base, the main portion B of which constitutes the base proper
of the machine and is provided with an upward extension B in which the head
supporting portion B³ is contained; said portion B being vertically adjustable in
its socket or bearing B2 in the base portion of the column and resting upon an
adjusting screw C, (see Figure 3) working in a suitably threaded bracket or bridge
portion of said base B. Said base B is also provided with a vertical bed or
guide-way B (see also Figures 13 and 14) upon which is secured the horn
support D, said horn support being capable of vertical adjustment on the said
bed 135 and being securely fastened when properly adjusted by means of bolts D³
which pass through slots in said horn support 1 to provide for said vertical adjust-
ment, as best shown in Figure 13.
The lower part of the head supporting column B3 is provided with an arm or
projection E which engages with the horn support 1 (see Figures 3 and 4) and
thus maintains the said horn support at the proper height with relation to the
head of the machine when properly positioned in the base B. The upper portion
of the socket 132 for the column 133 is longitudinally split as indicated at 13 20,
Figure 3, and provided with clamping bolts 12 by which the column B may be
rigidly fastened when set at the proper height.
By these means the working parts of the machine which require the especial
attention of the operator may be set at the height most convenient for a given
operator and if it is necessary at any time to change or readjust the height this
can be done by loosening the clamping bolts B2 D2, and then turning the screw C
up or down until the desired height is reached, the corresponding adjustment
being made in the connections between the working parts in the head and horn
and in the base portion B, which connections are constructed to provide for such

page_text: adjustment as will be hereinafter described. When the machine is set to the
desired height the bolts B20 D2 are again tightened.
The lower portion B30 of said column 133 is flattened as shown in Figures 3 and 4
and engaged by adjusting screws B by which the column B³ may be adjusted
angularly to bring the driving mechanism to the proper position with relation to
the horn or work support.
In order to provide for the accurate adjustment of the working devices of the
head with relation to the tip of the horn the frame A of the head is adjustably
supported upon the upper end of the column B3, being retained in alignment
therewith by a tenon or projection A15 (see Figures 1 and 5) entering a correspond-
ing groove in the upper end of the column, said tenon having a notch A (see
Figure 1) which is engaged by a collar A17 on an adjusting screw A18 (see
Figure 3) in the upper end of the column, whereby the head may be moved back-
ward and forward on the top of the column until the plane of the awi and driver
are brought into exact coincidence with the axis of the horn, after which the
head is securely fastened by the bolts A19 (see Figure 5) which pass through
elongated openings in the base flange of the head frame to admit of the said
adjustment.
The horn F is supported to rotate freely and be longitudinally movable in the
horn support D is normally pressed upward by a spring G (see Figure 14), the
upper end of which engages with a shoulder F2 inside of the shank portion 3 of
the horn, while the lower end of said spring rests upon a collar G2 engaging
through an anti-friction device G3 with a shoulder upon a foot piece G adjustable
vertically in the horn support 1) to thereby adjust the tension of the spring. The
said foot piece or spring support is externally threaded and engaged with a corres-
pondingly threaded socket in the horn support to provide for the vertical adjust-
ment, the said socket being split and provided with a clamping screw G as shown
in Figures 13 and 14 to lock said spring support when properly adjusted.
The upward movement of the horn by the spring G is limited by a shoulder or
collar H secured to the lower end of the horn shaft and resting through the inter-
vention of an anti-friction device H2 against a collar or ring H³ which itself rests
against the lower end of the portion of the horn support in which the shank of the
horn is rotatably mounted, there being preferably a yielding washer or cushion
interposed between said ring H3 and said bearing portion.
}
The collar H is connected with the horn shank by a screw thread so as to be
vertically adjustable thereon to adjust the height to which the horn may rise when
no material is supported thereon, said collar or ring H being divided transversely
and provided with a clamping screw H to hold it securely when properly
adjusted.
The ring H³ is connected by rods H+ (see Figure 13) with a forked link H
connected with a treadle or foot lever He (see Figure 3) by which the horn may be
depressed against the stress of the spring, as required in applying the shoc
or removing it therefrom.
thereto
The connection. H7 between the rods H and link H5 provides for adjustment
in the connection between the treadle and the horn as is necessary when the horn
support is adjusted vertically on the base of the machine, as has been, before
described.
The anti-friction bearings G3 H2 enable the horn to turn easily in its socket,
although subjected to considerable pressure by the spring. The socket or bearing
proper for the shank of the horn is split longitudinally and provided with bolts K
by which it may be adjusted to take up wear, in order that the horn shank may be
held firmly in upright position, while capable of rotating freely, it being essential
to the perfect operation of the machine that the tip or upper end of the horn work
or support proper should remain always accurately located upon the stock from
pegging mechanism proper, or awl and driver which operate upon the stock from
above.
"
It is necessary for good work that the insole should be supported close to the

page_text: point at which the awl and peg penetrate, as otherwise the material of the insole
will be depressed around the peg rendering the inner surface of the shoe uneven
and also precluding a close and compact union between the outsole, upper, and
insole, such as is necessary for good work.
In order to insure such support for the insole at the point where it is
penetrated by the awl and peg, the horn tip which contains the cutting devices,
which will be hereinafter described, is provided with a supporting top herein
shown as a cap or cover a (see Figures 17 and 20) provided with a central opening
or perforation a concentric with the axis of rotation of the horn and of sufficient
size to receive the protruding end of the awl or peg when substantially in line with
the axis of rotation of the horn. The said top or cover a for the upper end of the
horn is preferably a detachable piece and is thin at the sides of the opening, so
that the cutting jaws b which work close to its under surface may cut off the pro-
truding end of the peg close to the surface of the insole, thus leaving the said
surface of the insole sufficiently smooth along the line on which the pegs are
driven.
The peg cutting device as herein shown is composed of a pair of cutters b
operating like the well known cutting pliers or nippers, the jaws in the construc-
tion shown in Figures 18 and 20 being pivoted on a stud or pivot piece 62 secured
in the horn tip, and acted upon by springs 63 (see Figure 18) which tend to hold
the cutting jaws separated. The cutting jaw levers are provided with cam
surfaces 64 which receive between them a cam or wedge 65 capable of longitudinal
movement in the horn tip, which cam when moved upward or towards the pivot
of the cutter jaws separates the lower ends of the cutter levers, and thus closes
together the upper ends thereof carrying the cutters, which thus nip off the pro-
truding end of the peg between them at the under surface of the horn cap a.
It is not essential so far as the other features of the invention are concerned or so
far as the cutting device enters as an element in combination with other elements
of novelty in the machine that the cutters should be constructed and operated as
has just been described, and in Figures 21 and 22 a modification is shown in which
the cutting jaws 610 instead of being pivoted in the horn tip are movable bodily
in the horn tip, being closed by a movement of the operating shank or spindle 660
towards the end of the horn tip and opened by a movement of said shank in the
opposite direction.
In this construction the cutter blades 610 have their outer upper ends curved
and engaged with a correspondingly curved surface in the horn tip so that as the
blades are moved upwardly or towards the end of the horn their cutting edges are
crowded together by the cam or wedge action of the said engaging surfaces. The
end of the spindle 600 is recessed to receive the shanks of the cutter blades which
are provided with projections 620 confined between projections 621, 62 of a plate 683
secured as by a screw 621 to the upper end of the spindle 600 which is properly
recessed as shown to receive the said plate and the ends of the cutter blade shanks.
A plate 625 fastened as by a screw 626 to the horn tip further serves to confine the
cutter blades in working position in the horn tip, affording sufficient freedom for
the up and down movement of the cutter blades by the spindle 660 and the closing 4
together and separation of the cutting edge by a rocking movement of the cutter
shanks produced by such up and down movement.
Referring to the plane through the axis of the horn shank and through the part
of the horn laterally projecting therefrom as the plane of the horn, the pair of
cutting jaws operate in a direction at right angles to the plane of the horn each 5
jaw moving towards and from the axis, and the two jaws meeting at the axis of
the horn when the peg is finally severed. This construction is of importance,
since a pair of cutting jaws operating in this matter produces equal pressure on
opposite sides of the peg tip being cut, and consequently sever said peg tip without
any tendency to shift the position of the shoe or to break the peg itself as is the 5
case when a cutter operates from one side only of the peg.
The cutting jaws are supported in a tip F made in a separate piece from the

page_text: main portion of the horn F and having a shank F which is secured in a socket
in the main portion of the horn.
Thus the horn tin and cutters contained therein may be conveniently removed
and replaced by another if there is any occasion to do so, and in the construction
shown in Figures 18 and 19 there is no connection between the cutters and their
actuating spindle 6 which requires any attention when such exchange of horn
tips is made.
It is essential that the cutting device should be operated at the proper time at
cach complete operation of the peg driving mechanism so as to cut off the protrud-
ing end of the peg after it is driven by the descent of the driver and before the
feed of the material takes place preparatory to the driving of the next peg.
Such operation of the cutting device is provided for by connections through the
horn and column or base of the machine to the peg driving mechanism in the
head of the machine, such connections being properly constructed to provide for
the free and complete rotation of the horn upon its axis in the horn support B
and also for the adjustment of the height of the working parts of the machine
with relation to the base or column B, before referred to and being as follows:-
The cutting edges, as before stated, are closed and permitted to open by the
longitudinal reciprocation of the shank or spindle 6, Figures 15 and 18, (or 660,
Figures 21 and 22) longitudinally movable in the shank portion F³ of the tip F
of the horn.
The said rod 66 (or 660) is reciprocated longitudinally at the proper time during
each cycle of movements of the peg driving mechanism by means of a connecting
rod c, see Figure 15, connected with an arm c21, see Figures 15 and 16, from the
rock shaft in the lateral arm F6 which connects the horn proper with its shank
or bearing portion F³, said rock shaft being provided with a second arm c
connected with a rod 5 extending through the shank portion of the horn and
having fixed thereon near its lower end a grooved collar or hub co, see Figures 13
and 14, into the groove of which project studs. c7 guided in grooves in the horn
depressing link H5 before mentioned, and connected with links c¹0 themselves
pivoted at ca in the said horn depressing link H. The said links coc¹0 thus con-
stitute a toggle lever connection between the horn depressing link H (which
accompanies the horn in its vertical movement and thus remains in fixed relation
to the horn whatever may be its height dependent upon the thickness of the stock
in the operation of the machine) and the cutter actuating rod c, which owing to
the engagement therewith of the studs e' through the intervention of the grooved
collar permits of the swivelling movement of the horn without interfering
with the longitudinal movement of said rod by the said toggle lever c clo. The
collar c is adjustable upon the rod and is secured thereto when properly adjusted
by a clamp 60, thus providing for the adjustability of the height of the horn con-
taining the cutter and actuating mechanism therefrom to and including said rod c³
with relation to the base of the machine and the link or stirrup H5 and treadle
mechanism therefor supported on said base.
The toggle lever cc10 is straightened to close the cutting jaws and is bent or
broken to open the said cutting jaws by means of a link or connecting rod d best
shown in Figure 3 connected with one arm of an elbow lever pivoted at d³ in
the base B and having its other arm connected by a rod or link with actuating
mechanism in the head of the machine, by which said rod d is reciprocated longi-
tudinally at each rotation of the main shaft of the peg driving mechanism; or,
in other words, at each cycle of operations of the pegging machine, by which the
material is fed, prepared to receive a peg, and the peg driven.
The said link or connecting rod d is provided with a slip joint connection and
clamp as indicated at doo, Figure 3, to provide for adjustment of the length between
its upper connection with the working parts of the peg driving mechanism proper
and its point of connection with the lever d in the base B of the machine, when
the height of the working mechanism is changed with relation to the base, as
before described.

page_text: The connecting mechanism for operating the cutting devices in the horn is so
constructed and arranged as not to interfere with the complete rotation of the horn
so that the latter may be manipulated with perfect freedom, and may be turned as
far as need be by the operator of the machine, it being commonly desirable if not
necessary to turn the horn completely around during the presentation of each shoe
to the pegging devices.
It is obvious that the apparatus thus far described might be employed in con-
nection with peg driving or nailing mechanism of various kinds, and that the
invention embodied in the parts of the machine thus far described is not limited
to its embodiment in conjunction with any specific form of peg driving mechanism
except in so far as the latter embodies novel features of construction and operation,
which adapt it especially to co-operate with the material supporting and peg
cutting mechanism thus far described.
The stock feeding and peg driving mechanism which will now be described
embodies novel features of construction and mode of operation, which are of
special advantage in conjunction with the work supporting and peg cutting devices
thus far described, but some of which are also useful in connection with other forms
of work supporting mechanism either with or without means for cutting off the
protruding ends of the pegs when driven..
As before stated, it is essential for good work that the material should be
supported by the anvil or work support closely around the point at which the awl
penetrates and the peg is driven. This precludes the adoption of the awl feed as
heretofore commonly employed in pegging machines, in which the awl is rigidly
secured in the awl stock and penetrates to its full depth so that the awl stock bears
upon the outsole and depresses it below the presser foot or upper work clamp of
the machine before the lateral movement of the awl to feed the material takes place.
In accordance with the present invention, the awl instead of being fixed in an
awl bar the end of which descends into engagement with the outsole, is longitudin
ally movable in a nose or awl guide, and means are provided for giving the awl
and nose independent movement towards and from the sole, in conjunction with the
necessary lateral movement for the awl feed, these parts being so constructed and
operated that the awl is not entered into the material far enough to penetrate or
pass below the lower surface of the material at its thinnest point, at the time when
the awl guide is depressed and the lateral feed movement takes place.
When the awl is thus entered in but not passed wholly through the material,
the awl guide or nose descends so as to bear upon the outsole, depress it below the
presser foot or upper work clamp member, and thus free it from the hold between
the said presser foot and the horn below, after which both the awl and its guide
move laterally feeding the material to the point at which the awl is directly over
the axis of the horn.
It is preferable that the complete descent of the awl to penetrate the material
order to enable the peg to be properly driven, and an additional downward longi-
tudinal movement of the awl must be had either before or after the feed move-
ment takes place during which feed movement, the awl as before stated, does not,
pass wholly through the material, and consequently does not collide with the horn.
It is preferable that the complete descent of the awl to penetrate the material
should take place after the feed movement is completed, at which time the awl is
directly over the perforation 2 in the horn tip, as with such mode of operation
the radius of the supporting end of the horn tip may be greater than the length
of feed movement, and as herein shown the awl is caused to have a further
longitudinal downward movement after the lateral movement is completed, and
when the awl is directly over the axis of the horn, after which both the awl
and awl guide are raised, leaving the material clamped between the
horn aud presser foot, and are moved laterally back to their original position, in
which movement the peg and driver are brought over the awl hole, and the
peg is then driven at the point directly over the axis of the horn so that its pro-
truding end may be cut by the cutting device in the horn, previously de-cribed.
i

page_text: As herein shown the above mentioned elements are constructed for operation and
are operated as above described by the following mechanism best shown in Figures 1
to 12 inclusive:-
The machine is provided with a loose belt pulley e, Figures 1, 6 and 7, and a
driving pulley both adapted to turn freely upon a bearing support or spindle e³
in line with the main actuating shaft f of the machine. The said driving pulley
is connected with the shaft f by a clutch and stop mechanism of novel construc-
tion, best shown in Figure 1 and Figures 6 to 9 inclusive.
Said clutch comprises a friction member f³ itself loose and longitudinally mov-
able on the main shaft f, but engaged with a cross head f* thereon so as to rotate
said main shaft when it is itself rotated by the pulley ². The said clutch
member f3 has a friction surface adapted to engage with a socket f in the frame
to act as a brake to stop its rotation and that of the main shaft when disengaged
from a similar friction surface e on the driving pulley. Said clutch is moved
into engagement with the driving pulley or with the friction brake by a shifting
lever f pivoted at fo upon the main frame and engaged at its upper end with a
grooved hub 30 on the shiftable clutch member f³, its lower end being acted upon
at one side by a spring pressed plunger f7 tending to force the clutch member into
engagement with the driving pulley so as to set the machine in operation, and
acted upon at the proper time in opposition to said spring connection by a trip or
trigger pivotally connected with the lower end of said shifting lever f, which
trip when in its upper position is engaged with a stopping lever operated by a
cam fo on the main shaft f which cam at each rotation of the main shaft moves
the lever f, so that if the trip f8 is engaged therewith the clutch member f³ will
thereby be disengaged from the pulley and stopped by engagement with the
brake f
Engagement of the trip 8 with the lever f is controlled by a treadle f12, see
Figure 3, connected with said trip by a rod or link f provided with a slip joint
at f, see Figure 3, for adjustment when the head of the machine is raised or
lowered as before described.
When the treadle f12 is depressed the trip f is disengaged from the lever f³ and
the clutch is thrown into engagement by the spring f of the plunger f7 and the
machine runs continuously but when the said treadle f12 is released the trip f
tends to move upward and at the proper time in the vibration of the lever f slips
past and into engagement therewith as shown in Figure 1, so that when the lever
is vibrated in the proper direction by the cam f10 the clutch will be disengaged and
the main shaft stopped at a definite point dependent upon the position of the
cam f10 on said main shaft.
The trip arm and stop lever fare provided with suitably hardened engaging
fingers clamped in sockets in said levers, and said projection 80 in the trip arm
is provided with a threaded shank or stem, see Figure 9, co-operating with a
nut in a recess in said trip arm whereby the end of the projection may be
properly adjusted to cause the clutch member f³ to engage properly with the
brake f³.
The machine is thus stopped when the awl and awl guide are disengaged from
the outsole, thus leaving the shoe free to be withdrawn from the machine and the
machine in proper condition to receive the next shoe and to begin operation there-
on when the clutch is again engaged by depression of the treadle fi
The bearing support for the fast and loose pulleys e2 is shown as a dead or
non-rotating spindle, and the driving pulley is secured by screws e20 (see
Figure 6) to a sleeve which furnishes the bearing for the loose pulley e.
Thus a long bearing surface is afforded for both pulleys. The spindle e³ is
hollow and is provided with an oil inlet duct 30, and suitable perforations are made
in said spindle and in the sleeve e, to distribute the oil over the internal and
external bearing surfaces of the sleeve, which is confined from longitudinal move-
ment on the spindle e by a collar fastened to the inner end of the spindle as
shown.

page_text: :
The other end of the sleeve e21 and of the hub of the loose pulley e
is engaged
by a washer e resting against a shoulder on the spindle e as shown in Figures 6
and 7, and the said spindle is held fast in a suitable bearing socket A30 in the main
frame work of the head, said socket being split and provided with a clamping
bolt A31 (see Figures 1 and 7) to hold the said spindle firmly.
The spindle may be adjusted longitudinally in its bearing socket to bring the
driving pulley in proper proximity to the clutch member f³, a screw having a
collar engaging with the end of the spindle as shown in Figure 7 serving to
facilitate said adjustment.
.
By having the pulleys run on a shaft or bearing independent of the main driven
shaft, the momentum of the moving parts when disengaged from the driving
pulley is reduced to a minimum.
The awl, awl guide, and peg driver receive the proper movement from the main
shaft through suitable cams thereon as will be described. The awl 9, see Figure 5,
is fastened in an awl bar and works through a nose or awl guide h secured to a
slide bar h2, the said bars and h2 as well as the driver bar of the driver i all
being longitudinally movable in a carrier k capable of lateral or transverse move-
ment in the main frame A of the head of the machine, said carrier & being pro-
vided with guide rods working in suitable guideways in said frame as clearly.
shown in Figures 1 and 5.
The carrier is slotted or recessed at its rear as best shown in Figure 6 and
provided with bearing pieces 3 preferably adjustable as shown, (see also Figure 11)
co-operating with a cam k at the end of the main shaft f, which gives the desired
lateral or feed movement to the carrier k and awl, awl-guide, and driver bars
working therein.
By having cam k operate positively on the carrier k to move the same in both
directions, and having the guides of said carrier substantially in the plane of
action of said cam as shown in Figure 6 a very rapid and easy running of the
machine is attained.
The cam as clearly shown in Figure 11 has two portions concentric with its
axis of rotation but at different distances therefrom, the difference in radius of the
two portions being equal to the length of feed movement desired, and said con-
centric portions are connected by curves such that the width between the tangent
faces of the bearing pieces is constant in all positions of the cam, which thus
engages positively at all times with both of the said bearing pieces, rendering
the movement of the carrier positive and uniform and without concussion.
If it is desired to change the length of feed of the machine the cam is
removed and another of the same character but with the difference between the
radii of its concentric portions equal to the new length of feed desired is sub-
stituted, the bearing pieces 3 being readjusted if necessary to contact with both
sides of the cam.
When the feed is changed, the position of the head of the machine is readjusted
if necessary to bring the awl over the axis of the horn at the end of the feed
movement, this being effected by the angular adjustment of the column 13 by
the screws B31 (Figure 4) above referred to, said angular adjustment of the column
affording a corresponding lateral adjustment of the end of the machine head
containing the awl and driver, in the direction of the feed movement.
This lateral adjustment of the portion of the machine head containing the awl
and driver in conjunction with the longitudinal adjustment of the machine head
on the column by the device A17 (Figure 3) before described enables the elements
of the pegging mechanism that act directly upon the material being pegged to be
adjusted accurately with relation to the horn, as is necessary for good work.
The driver bar is provided with a lug or projection engaged by a projec-
tion on the cam which operates to raise the driver at a definite time in each
rotation of the main shaft and then to release the same, permitting it to be driven
by an arm actuated by a spring contained in a spring barrel or holder 28, said
arm acting on the upper end of the driver bar through the intervention of a
4

page_text: connecting rod engaged with said spring arm and driver bar by a ball and socket
or universal joint to accommodate the various movements thereof, while retaining
the driver bar under downward spring pressure, so that it is thrown downward
when released by the projection when it arrives at the position shown in
Figure 11.
The construction of the spring and its connection with the arm 2 is best shown
in Figure 2. The said spring 7 is a spiral spring having the ends thereof bent
into line with its axis as shown at 270,271 and preferably squared or otherwise
adapted to be held securely against rotary movement.
The spring barrels 28 and the bearings for the driver actuating arm 26 are
supported in a bracket A10 extending from the frame A of the head of the machine,
and forked at its upper end to afford two annular supports A2 for the spring
barrels 28.
Within the openings of said supports are bushings which form the bearings
in which the hub of the driver arm 26 is supported, said bushings being provided
at their outer ends with flanges by which they are clamped in position by the
spring barrels 28 which are secured by bolts 213 to the bearing supports A¹²
The squared ends 271 of the springs are fitted in a correspondingly shaped
socket in the axis of the hammer arm 2, and are securely held therein by bolts 272
while the outer ends 270 of said springs are similarly held in the ends of the spring
barrels 28 so that said springs acts torsionally upon the arm 26 tending to force the
same downward.
The bolts 13 by which the spring barrels are fastened to the supports A12 pass
through curved slots in said spring barrels as clearly shown in Figure 1, so that
the latter may be adjusted angularly with relation to the said supports A12 before
being fixedly held with relation thereto by the bolts 23, thus enabling the tension
of the springs to be varied.
The springs and the corresponding parts at the two sides of the support A10
are merely duplicates of one another, and a single spring similarly constructed, at
one side only of the driver arm might be used, although the construction shown is
preferable as being more compact and symmetrical.
The awl bar is operated in its up and down movement by an arm or lever g
having a slotted end co-operating with a pin or projection from said awl bar as
shown in Figures 5 and 10, said arm being fixed to one end of a rock shaft g',
the other end of which is provided with an arm (see Figures 1 and 12) operated
by a slide g forked or slotted to embrace the main shaft f, as shown in Figure 12
and provided with a cam roller g' engaging with the cam groove in the cam g³ on
the main shaft.
The arm g3 is angularly adjustable on the rock shaft which is provided with a
radial pin or projection go, Figure 5, keyed therein and engaged by set screws 930
in the arm g, which is split and provided with a clamping bolt g³ to fasten it
securely on the rock shaft when set at the proper angular position with relation
thereto, (see Figure 5).
This construction enables the point of the awl to be set at the proper height to
properly enter, penetrate, and be wholly withdrawn from, the material under the
action of its cam g³.
The arm is longitudinally slotted and the connecting joint between the same
and the slide 6 is adjustable in said slot towards and from the rock shaft g' to
thus vary the throw or longitudinal movement of the awl as may be desired.
The slide works in a guide in a cap g loose on the main shaft and covering
the grooved face of the cam 78 as best shown in Figures 6 and 10.
The groove of
the cam g that operates the awl bar is constructed with a double throw as shown
in Figure 12 in which the roller g7 is in the part of the groove that retains the awl
at its highest position or wholly withdrawn from the material, said groove having
a portion which operates to depress the awl a certain distance, and is followed
by a portion 981 which causes the awl to dwell in its partially depressed position
(at which time the lateral feed movement of the carrier k takes place) followed by
B

page_text: a portion which causes the complete descent of the awl to take place by which
it wholly passes through the thickest part of the material at any time operated
.upon.
The awl guide h has a vertical movement by which its lower end is raised above
and depressed below the level of the presser foot P', the said depression taking
place before the beginning of the feed movement and causing the horn to yield
downward against the stress of its spring G so as to free the sole from the presser
foot and enable it to be fed along the top of the horn by the lateral feed move-
ment of the awl and its guide effected by the carrier k as before described.
This up and down movement of the awl guide h, which is independent of the up
.and down movement of the awl itself is produced by a lever 3 pivoted at * on the
frame work and having one arm engaged with the upper end of the awl guide
bar 2, and its other arm provided with a cam roller adjustably secured thereto
as shown in Figures 10 and 12 and co-operating with the periphery of the cam 98,
which, as shown in Figure 12 depresses the said awl bar guide at about the time
when the awl receives its preliminary downward movement and retains it depressed
until the awl has completed its downward movement, after which the awl and
its guide are both raised to their highest position, thus withdrawing both from the
sole which is then forced up by the horn against the presser foot P and clamped
firmly between the horn and presser foot, while the carrier k makes its return
movement which brings the peg and driver over the awl hole just before the
driver is released by the projection and caused to driver the peg. The awl-
guide is lifted by the spring 20, (see Figure 5).
The cutter actuating mechanism for the peg tip cutter in the horn is operated
at the proper time, that is just after the peg is driven, by an arm , see Figure 9,
connected with the upper end of the connecting rod before mentioned. Said
arm is connected with the fulcrum shaft f4 of the clutch operating lever f9,
and thus operated by the cam f10 before mentioned which operates to disengage
the clutch, the effective movement of the cutter thus taking place just before the
point at which the machine stops when thrown out of operation.
The peg wood 7, see Figures 23 to 25, is fed by novel means comprising a peg
wood guide rigidly secured to the laterally moving carrier & for the awl and
driver bar at the rear thereof as best shown in Figure 25.
3
The peg wood feed roll is journalled in said guide and is provided with a
ribbed surface to engage one side of the strip which is acted upon at the opposite 3
side by a correspondingly ribbed presser roll 3 mounted in a bearing piece capable
of longitudinal movement in a socket 10 in the peg guide and acted upon by a
spring to press the roll against the peg wood, the shank of the bearing piece of
the roll being provided with a stop shown as a nut (32 and lock nut 33, see
Figure 23, to limit its movement under the action of its spring.
4
The feed roll 2 is provided with a ratchet 1, the teeth of which are properly
spaced to advance the peg wood enough for one peg as the ratchet is advanced one
tooth, such ratchet being detachable and secured to the feed roll by a screw t¹ so
that it can be exchanged for one with longer or shorter teeth when the
peg
wood
feed is to be varied. The ratchet is advanced one tooth at each to and fro vibra- 4
tion of the carrier of the awl and driver by means of a pawl 5 pivoted at to in
a slide 5 movable in a guide passage to secured in the frame of the machine, said
slide being acted upon by a spring as best shown in Figure 23 tending to keep
its pawl carrying end in engagement with the end of the guide 52 as shown in
Figure 23.
The rotation of the peg wood feed roll takes place in the latter part of the return
movement of the carrier k after it has moved to feed the stock and is returning
to bring the driver over the awl hole, the peg wood being fed forward just as the
driver comes into position over the awl hole immediately before the driver descends
to drive the peg, the parts then being in the position shown in Figure 23.
In the forward or stock feeding movement of the carrier k the end of the peg
strip which was advanced at the previous return movement of the carrier as has
5
5

page_text: been just described, is cut off by coming against the edge of a knife which is
fastened to the frame of the machine as best shown in Figure 5, and in this move-
ment of the carrier the peg wood feed roll, which is prevented from rotating by
a brake or spring 2 (see Figures 23 and 24) pressing frictionally against the shaft,
passes the end of the pawl to which engages the next tooth of the ratchet ready to
advance the same at the next return movement of the carrier.
In order to insure that the pawl 5 shall pass but one tooth only of the ratchet.tt
in this movement, whatever may be the length of the travel or feed movement of
the carrier, the said pawl is caused to accompany the ratchet after the latter has
moved past the pawl a distance equal to or a trifle greater than the length of one
tooth of the ratchet. To effect this the peg wood guide piece t is provided with a
shoulder or projection y shown as a head or enlargement at the end of a bolt
screwed into the peg wood guide for the purpose of adjustment, said shoulder
engaging with a corresponding shoulder y on the pawl carrier or slide which
after such engagement is drawn along by the further movement of the carrier k
against the pressure of the spring 3, which in the return movement of the carrier
causes the pawl to travel with the ratchet until the pawl carrier tal brings up on
the end of its guide t, after which the further movement of the pawl and driver
carrier k causes the ratchet to turn and the peg wood to be fed.
This construction insures that the peg wood feed ratchet is advanced one tooth,
and one tooth only, at each to and fro vibration of the awl and driver carrier what-
ever may be the extent of said vibration depending upon the length of feed
desired for the material between consecutive pegs, it being necessary only to adjust
the engaging shoulder y to correspond to the size of the ratchet teeth at any time
used for feeding the wood.
peg
In order to guide the shoe during the pegging operation, the machine is provided
with a gauge r, see Figures and 26 to 29, which engages with the periphery of
the sole and maintains it at a definite distance from the line of action of the awl
and driver during the pegging operation.
It is common in pegging shoes to drive parallel rows of pegs around the sole or
a portion thereof, and is therefore necessary to guide the shoe in two different
paths for driving the two rows of pegs. The gauge is in accordance with this.in-
vention provided with a shifting device by which it can quickly be thrown from
one to the other position, according as the pegs are to be nearer to or farther, from
the edge, without interrupting the operation of the machine.
The gauge proper is shown as a horizontal roller supported at the end of a
carrying bar or shank which is itself adjustably secured to a slide by screws
passing through longitudinal slots in said shank 2 as indicated in dotted lines
Figure 28.
The slide 3 works in a guideway provided with a shank 6 detachably secured
and vertically adjustable in a socket in the main frame A by a set screw ri, see
Figure 1, the position of said guide being determined by a steady pin also
entering a suitable socket in the main frame. Thus the gauge may be raised
or lowered with relation to the presser foot I', or may be wholly removed from the
machine if desired.
The slide is normally pressed to the rearward by a spring 30, see Figure 29,
bearing against a plunger which in turn bears against a stud at the rear end of
the slide, the rearward movement of which is limited by the lower end of the
steady pin entering a slot in the slide. Thus with the slide in its rearmost
position indicated by dotted lines Figure 29, the gauge may be set by adjusting
the bar on said slide to give the maximum distance for the pegs from the edge
of the shoe as in pegging the inner row of pegs.
In order to move the gauge to the nearer position for pegging the outer row of
pegs, the slide is provided with cam 10 (see Figure 29) operated by a handled
lever or shifting device having its fulcrum at 3 in a fulcrum piece.
+
When the lever is disengaged from the cam as shown in dotted lines Figure 29
the slide and gauge are thrown rearward by the spring until arrested by, the

page_text: pin at the end of the slot but when the said handle lever is thrown against
the said cam it forces the slide forward until the handle lever comes to rest in the
notch or shoulder formed at the end of the cam 10 as shown in Figure 29 when it
positively resists the rearward movement of the slide and gauge and remains
locked thereto until positively thrown out of the notch by the operator.
In order that the distance between the forward and rearward positions of the
gauge, and consequent distance between the rows of pegs, may be varied as required
in different kinds of work, the fulcrum piece for the gauge shifter 712 is
adjustable, being pivotally connected at 5 with the guideway and provided at
its other end with a screw or clamping device 1 engaging with the guideway of
the slide in a curved slot 750 (see Figure 26), so that the outer end of the fulcrum
piece 14 may be swung around its axis at 15 thus moving the fulcrum 13 of the
shifting lever forward or back, so that the said shifting lever will throw the slide
a greater or less distance forward when turned into engagement with the cam 10.
Suitable gauge marks or graduations are provided along the edge of the gauge
guide as shown in Figures 1, 26 and 28, to indicate the positions at which the
fulcrum piece r should be set for different distances desired between the rows of
pegs.
While the hereinbefore described mechanism for actuating the working parts
of the machine, viz. awl, driver, and peg tip cutting device, are extremely simple,
compact, and efficient, it is obvious that various modifications might be made
therein without departing from the essential features of the invention, and other
mechanism for giving the essential novel movements of the awl and awl guide and
elements that co-operate therewith to perform the essential operations of pegging
are regarded as substantially equivalents for those herein shown and described.
Having now particularly described and ascertained the nature of the said in-
vention and in what manner the same is to be performed, as communicated to me
by my foreign correspondents, I declare that what I claim is:
1. The combination of a rotatable horn or work support provided with a work
.supporting surface, and with a pair of cutting jaws both movable with relation to
said surface, and actuating mechanism therefor, substantially as described.
2. The combination of the rotatable horn or work support, with a pair of cutting
jaws operating in a direction transverse to the plane of the horn, both of said jaws
being movable towards and from the axis of the horn, and actuating mechanism
therefor, substantially as described.
3. The combination of the rotatable horn, with a removable horn tip and cutting
device supported and operating in said horn tip and removable therewith from the
horn, substantially as described.
4. In a pegging machine a vertically movable horn or work support capable of
complete rotation and having a tip or cover provided with a central perforation
concentric with the axis of rotation of the horn, combined with a cutting device
supported in said horn and operating below said perforation in the tip thereof, and
peg driving mechanism, and connecting mechanism substantially as described
between said peg driving mechanism and said cutting device whereby the latter
is operated at each peg driving operation unaffected by the vertical and rotary 4
movement of the horn, substantially as described.
5. The combination of the horn or work support, and a peg-tip cutting device
therein, with a pegging mechanism comprising a peg driver, and an independently
movable awl and awl guide, and means for moving the same laterally to feed the
material; and actuating mechanism for producing independent longitudinal 5
movements of said awl and awl guide, substantially as and for the purpose
described.
6. The combination of the presser foot and vertically yielding horn or work
support, with a pegging mechanism comprising an awl and peg-driver, and means
for moving the same laterally and depressing the material from the presser 5
foot to feed the material, and actuating mechanism for producing a partial longi-

page_text: tudinal movement of the awl whereby it enters the material; but does not project
therethrough during the lateral feed movement of the awl, and is caused to pass
wholly through the material when said lateral feed movement is not taking place,
*substantially as described.
7. The combination of the awl and independently movable awl guide with
actuating mechanism for producing independent longitudinal movements of said
awl and awl guide, substantially as described.
8. The combination with a yielding upwardly pressed work support and a
presser foot or work clamp co-operating therewith, of an awl and awl guide and
laterally moving carrier therefor, and actuating mechanism for producing a lateral
movement of said carrier, and independent longitudinal movements of said awl and
awl guide, substantially as described.
9. The combination of the horn or work support; with the pegging mechanism
comprising a peg driver, and an awl and independently movable awl guide, and
means for moving the same laterally to feed the material and actuating mechanism
for producing independent longitudinal movements of said awl and awl guide,
substantially as and for the purpose described.
10. The combination of the horn or work support having a tip provided with a
perforation, and a cutting device in said horn operating below the perforation in
its tip with a pegging mechanism comprising a peg driver, and an independently
movable awl and awl 'guide, and means for moving the same laterally to feed the
material; and actuating mechanism for producing independent longitudinal move-
ments of said awl and awl guide, substantially as and for the purpose described.
11. The combination of the rotatable horn having a tip provided with a central
opening concentric with the axis of rotation of the horn, of a pair of pivotally
connected cutting jaws operating in the horn tip below the opening thereof and
actuating mechanism for intermittingly operating said cutting jaws, substantially
as described.
12. The combination of the main supporting frame or base with a horn or work
support and supporting bearing therefor, vertically adjustable on said base, and a
machine head supporting column also vertically adjustable on said base, substan-
tially as described.
13. The combination of the main supporting frame or base with a horn or work
support and supporting bearing therefor, vertically adjustable on said base, and a
machine head supporting column also vertically adjustable on said base, and
engaged with said horn whereby equal vertical adjustment of the machine head
and horn is secured, substantially as described.
14. The combination of the horn or work support, of the peg driving mechanism
comprising an awl and driver, and actuating mechanism and a supporting frame
therefor, and means for adjusting said frame of the peg driving mechanism in a
horizontal direction on the supporting column whereby the plane of the awl and
driver may be brought into proper alignment with the horn, substantially as
described.
15. The combination of the rotatable horn and supporting bearing therefor
with a non-rotating horn depressing link, a cutter in said.horn and actuating
connections therefor comprising a rod passing through the shank of the horn and
rotating therewith, and an actuator for said rod having a bearing support in said
horn depressing link, substantially as described.
16. The combination of the horn bearing with the horn having a shank
rotatably supported in said bearing, a spring contained in the shank of the horn
and engaged at one end therewith, a support for the other end of the spring, an
annulus fixed to the horn shank below the lower end of its bearing socket, and an
annulus loosely encircling the horn shank between the annulus fixed thereon and
the lower end of the bearing socket, and means connected with said loose annulus
for depressing the horn against the stress of the spring therein, substantially as
described.
17. The combination of the horn bearing, with the horn having a shank

page_text: :
rotatably supported in said bearing, a spring contained in the shank of the horn
and engaged at one end therewith, a support for the other end of the spring, an
annulus fixed to the horn shank below the lower end of its bearing, and
an annulus loosely encircling the horn shank between the annulus fixed
thereon and the lower end of the bearing, means connected with said loose
annulus for depressing the horn against the stress of the spring therein, and an
anti-friction bearing between said loose annulus and said fixed annulus, and an
anti-friction bearing at one end of the spring, substantially as described.
18. The combination of the material feeding and peg driving mechanism of a
pegging machine, with a gauge for the material to be operated upon, a spring
pressed slide for said gauge provided with a cam having a locking shoulder, and a
gauge shifter co-operating with said cam whereby said slide is shifted and locked
against the stress of its spring or released for movement by its spring, substantially
as described.
19. The combination of the material feeding and peg driving mechanism of a
pegging machine, with a gauge for the material to be operated upon, a spring
pressed slide for said gauge, and a shifting lever for said slide, and adjustable
fulcrum piece for said shifting lever, substantially as described.
20. The combination of the material feeding and peg driving mechanism of the
pegging machine, with a gauge for the material to be operated upon, and means
for connecting the same with the frame work of the pegging mechanism having
provision for vertical adjustment with relation thereto, substantially as described.
21. The combination of the horn or work support, with the peg driving
mechanism comprising an awl and driver, an actuating mechanism and supporting
frame therefor, and means for adjusting the said frame of the peg driving
mechanism with relation to the horn in a direction at right angles to the plane
through the awl and driver and also in the direction of the said plane whereby
the awl and driver may be accurately located with reference to the axis of the horn,
substantially as described.
22. The combination of the awl and driver, with a carrier therefor having a
rectilinear vibrating movement and provided with opposite cam engaging surfaces,
and a cam interposed between and engaging with said surfaces, having
portions of its periphery concentric but of different radius and connected
by curves such that the distance across the cam between opposite tangential engag-
ing surfaces is constant for all positions of the cam, substantially as described.
23. The combination of the awl and driver, with a carrier therefor, and an
actuating cam continuously engaged at opposite sides with said carrier which is
provided with adjustable bearing pieces for engagement with said cam, substan-
tially as described.
24. The combination of the awl and driver bars and the vibrating carrier there-
for, with the feed cam engaged at opposite sides with said carrier whereby the
latter is moved positively in both directions, substantially as described.
25. The combination of the driver bar, with the actuating rocker arm therefor
pivotally supported in the frame and the actuating spiral spring and spring.
support, said spring having its ends in line with the axis thereof and secured in the
said arm and spring support respectively, and said spring support being adjust-
ably secured to the bearing support of said actuating arm, substantially as
described.
26. The combination of the awl bar and actuating rock shaft therefor provided
with a slotted arm, of the actuating cam and the slide actuated thereby and con-
nected with said arm in the slot thereof whereby the movement of the awl may be
varied, substantially as described.
27. The combination of the awl bar, with the actuating rock shaft therefor pro-
vided with arms, one connected with the said awl bar; and an actuating cam and
slide actuated thereby connected with the other arm of said rock shaft; and means
for angularly adjustin one of said arms on said rock shaft, substantially as and
for the purpose described.

page_text: 28. The combination of the awl and driver, with a carrier therefor provided with
guide pins and supporting guideways therefor, and the cam for positively
actuating said carrier in both directions, substantially as described.
29. The combination of the vibrating carrier and peg driver supported thereon,
with the peg wood guide supported on said carrier, and vibrating therewith, the
peg wood feed roll and ratchet on said carrier, and the pawl and pawl carrier co-
operating with said ratchet and means for engaging said peg wood guide and pawl
carrier whereby the latter may be caused to accompany the former during a portion
of its vibratory movement, substantially as described.
30. The combination of the peg wood feed ratchet and transversely vibrating
support therefor, with the pawl to and movable spring pressed pawl carrier 5,
said ratchet support and pawl carrier being provided with co-operating engaging
projections yy, substantially as and for the purpose described.
31. The combination of the driving pulley of the machine provided with a fric-
tion surface; with the main shaft, and a clutch member connected to rotate there-
with but capable of independent longitudinal movement thereon and provided
with friction surfaces at its opposite ends, and a stationary friction surface or brake
and means for moving said clutch member into engagement with the driving
pulley or brake, substantially as described.
32. The combination of the driving pulley of the machine provided with a
friction surface; with the main shaft, and a clutch member connected to rotate
therewith but capable of independent longitudinal movement thercon and provided
with friction surfaces at its opposite ends; and a stationary friction surface or
brake, and means for yieldingly impelling said clutch member towards engagement
with one of said friction surfaces, and means for positively moving said clutch
Imember into engagement with the other of said friction surfaces; substantially
as described.
33. The combination with the main shaft, of a clutch, member connected to
rotate therewith but capable of independent longitudinal movement thereon, and
provided with friction surfaces at its opposite ends, a stationary friction surface
at one side of said clutch member, and a driving pulley at the other side thereof,
and a bearing support for said driving pulley independent of the main shaft,
substantially as described.
34. The combination of the driving pulley of the machine, provided with a
friction surface; with the main shaft, and a clutch member connected to rotate
therewith but capable of independent longitudinal movement thereon and provided
with friction surfaces at its opposite ends; and a stationary friction surface or
brake; a cam on said driven shaft; and a trip arm adapted to be actuated by said
cam, whereby said clutch member is shifted from engagement with one to engage-
ment with the other of said friction surfaces, substantially as described.
35. The combination of the driving pulley of the machine, provided with a fric-
tion surface; with the main shaft, and a clutch member connected to rotate there-
with but capable of independent longitudinal movement thereon, and provided
with friction surfaces at its opposite ends; and a stationary friction surface or
brake, a cam on said driven shaft, and a trip arm adapted to be actuated by said
cam whereby said clutch member is drifted from engagement with one to engage-
ment with the other of said friction surfaces, said trip arm being yieldingly
pressed in the opposite direction whereby when disengaged from said cam the
clutch is shifted in the reverse direction, substantially as described.
71
1907
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C.
Agents for the Applicant,
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C.
Agents for the Applicant,