Improvements in Machinery for the Manufacture of Nails, Screw Blanks, Rivets, Bolt Blanks, and such like Articles.
Year: 1894

page_text: Date of Application, 29th Jan., 1894
Complete Specification Left, 11th May, 1894-Accepted, 9th June, 1894
PROVISIONAL SPECIFICATION.
Improvements in Machinery for the Manufacture of Nails, Screw
Blanks, Rivets, Bolt Blanks, and such like Articles.
I, ROBERT POWELL, of 5 Euclid Avenue, Cleveland, Ohio, in the United
States of America, Mechanical Engineer, do hereby declare the nature of this
invention to be as follows:-
My invention relates to an improved system of wire nail and such like machines,
in which several complete and independent sections, or nail or such like forming
mechanisms, are assembled or arranged in a small area and operated from a single
source of power through the medium of mechanism hereinafter described.
My invention consists broadly of the employment of a central source of power
and a number of transmitting members radiating from and actuated by the central
member and arranged to actuate any form of mechanism suitably arranged in
connection therewith.
My invention further consists in a wire nail and such like machine constructed
with a number of sections (each section constituting an operative machine in
itself) radiating from a common centre and so located as to be operated
simultaneously by the series of trans:nitting members which radiate from a central
source.
In my machine, the central power mechanism consists preferably of a main
vertically reciprocating actuating wedge, and power is communicated from this
main wedge through a series of radially reciprocating transmitting wedges to be
actuated.
The nail or such like forming dies are operated by the transmitting wedges, and
the other details in the operation are provided for, as well as means for throwing
out of action any number of the sections while the remaining ones are kept in
operation, as will hereinafter be described.
The central source of power consists of a plunger, which is hollow to secure
strength without unnecessary weight and is provided with a swell or bulge.
Radiating from the swell are wedge-ribs, and between these wedge-ribs the surface
of the swell may be vertical. A portion of the upper outer face of each wedge-rib
is vertical, but, from said vertical portion, the face of each rib is inclined inwardly
and downwardly to provide a wedging face. On each side of each rib are formed
flanges that are flush with or conform to the outer faces of the rib, which are
formed as just described. The wedge ribs and flanges hence constitute what I
will term hereinafter wedging "T-wings." The inclined outer faces of the T-wings
act as wedges, the vertical portion serving to permit lost motion, and the inner
sides of the flanges thereof act similarly but in the opposite direction, the outer
faces acting radially outward, and the inner faces acting radially inward as will
now be described. These wings may be formed integral with the plunger, but I
prefer to form them separately and attach them with bolts.
The plunger is guided in boxes on a suitable bed-plate and receives a vertical
reciprocating movement from a crank shaft working in a yoke attached to the
plunger, or by other suitable means.
The yoke has an opening for the end of the plunger, which is squared to fit said
opening and is secured therein by keys between the yoke and plunger recessed into
each. The parts are all secured in place by transverse bolts. The plunger also
has specially formed bearings at its lower end for guiding it vertically as it is
reciprocated by the crank. These bearings consist of grooves, in which work
corresponding ribs on the yoke. The ribs have tongue and groove connection with

page_text: the yoke, and this connection is made wedging for adjustment and taking up wear,
such adjustment being effected by screws.
The yoke has a sliding journal-box in which the crank of the main drive shaft is
journalled, and this journal-box has an adjusting wedge moved by screw for taking
up wear.
Any desirable number of sections or wire nail or such like machines are arranged
equidistantly in radial position in a bed plate common to all around the central
plunger, which operates them all simultaneously, and of these as many as desired
may be placed in operative connection while the rest are thrown out, as will
presently be explained. As the radial machines are all alike the description of
one of them will suffice to disclose and elucidate the construction and operation of
the entire combined machine. For each radial machine there is a Y-shaped
transmitting frame or member con rolled at its inner end by the central source of
power, as will be described, and having wedging arms for operating the nail or
such like forming dies, also with a hammer stock which also receives reciprocating
movement from the central source or wedge-shaped plunger. The Y-shaped
frame and hammer stock are forced radially outward by each descent of the
plunger and as the plunger moves up, the hammer stock and through it the
Y-frame are drawn in. This inward movement of the parts is transmitted through
the medium of side grips, which engage between T-wedges and which are connected
to the header block by a coupling to be hereinafter described, and which constitutes
the means of throwing the whole section into and out of operation. The extremities
of the arms of the Y-shaped frame are wedge-shaped and provided with flanged
plates engaging with the die blocks so as to force them together on the wire in the
outward movement of the Y-frame and to draw them apart by the inward
movement of said frame. The hammer stock carries a post projecting up through
a slot in the shank of the Y-frame, whereby the frame may be drawn in by the
block, and this slot is of sufficient length to permit lost or relative motion between
the frame and block. This lost or relative motion outward, is produced by
extending the operating face of the plunger shoe in a vertical plane, and providing
a corresponding vertical face at the lower part of the inner end of the frame, so
that when the Y-shaped frame completes its outward movement, it is held in its
extended position while the hammer stock continues to be moved outward. The
effect of these movements is to hold the gripping dies in their closed position on
the blank while the stock performs its work, after which, at the termination of the
outward movement of said stock, it is moved inward through the medium of grips
till the post strikes the inner end of slot, after which the stock and frame move
inward together, thus opening the dies and releasing the finished nail.
The
By making the wedge-shoes of the plunger separable, I am enabled to form them
of better or different metal and to replace them at small cost when worn.
inner end of the Y-frame is provided with a brass face to take the wear, said brass
face being set in a dove-tail so as to be easily replaced. A similar brass piece is
provided on the inner end of the hammer stock which receives its radial recipro-
cating movement from the lower wedge face of the plunger-shoe in the same way in
which the Y-frame receives reciprocating movement from the upper wedge fare.
The parts are suitably formed and arranged to simultaneously grip, cut and point,
and then to head the blank by a substantially continuous movement of the frame
and hammer stock. Between the hammer stock and the hammer operated thereby,
is a wedge adjusted by a screw so as to accurately set up the hammer to compensate
for wear and adapt it to operate effectively in heading the nail.
The hammer stock is adapted to reciprocate in suitable ways or guides on the
bed-plate. This stock is constructed as follows:-
This stock is formed with laterally projecting ribs, upon which are mounted side
grips which slide on said central section of the hammer stock. The inner ends of
these sliding side grips are provided with lips inclined to correspond to, and
engaging behind, the inner faces of the T flanges of the plunger rib or shoe with
which they engage. The inner end of the stock is inclined and is parallel with the

page_text: outer face of its opposing T-wing with which it engages. The outer end of the
stock is formed with a recess to receive the hammer or header. The Y-frame and
hammer stock are held together, but, so as to allow said relative movement, by
standard arms on the side grips extending upward and meeting above the stem of
the Y-shaped frame and stock and behind the post and securing said frame and
hammer stock together. At the same time the stock is secured to the bed plate by
guides so that all the parts are held down.
To the arms is swivelled the coupling, which consists of side links swivelled to
arms and to which a handle is trunnioned, said handle being fulcrummed or pivoted
on the post of the hammer stock.
It will be understood that the handle and coupling with the attachments described,
form the connection between the hammer stock, which receives the outward pressure
of the wedge surfaces in the downward movement of the plunger, and the grip_by
which the parts are drawn inward on the upward stroke of the plunger. The
adjustment of the bearing plate by the screw rod takes up lost motion produced by
wear between the operating flanges of the plunger and the bearing faces of the
hammer stock and grip on which they act.
In order to throw any one of the radial machines out of gear, it is only necessary
to throw up the gravitating handle, which movement, acting through the links,
throws the retracting flanges of the grip inward beyond the reach of the operating
flanges of the plunger shoe and thereby all the parts of this particular machine or
section are left at rest.
The wedging arms of the Y shaped frame have secured to them, so as to project
inwardly over their edges, plates, oblique or inclined inwardly from their outer
ends, parallel with the inclined inner edges of said limbs, and these flanges are
received by correspondingly inclined grooves in the die-blocks which also have
inclined or oblique edges parallel with the grooves engaged by the inclined or
oblique edges of said arms. By means of this construction, when the Y shaped
frame is reciprocated longitudinally by the inclined end of its stem, that is parallel
with the inclined face of the opposing plunger shoe, the dies of this respective set
will be caused to approach and recede from each other, and perform their
respective functions, the dies being forced together by the engagement of the
oblique edges of the die-blocks and the oblique edges of the arms and being drawn
apart by the oblique flanges working in the oblique grooves in the die-blocks. The
stem of the frame has a portion of its face inclined and a portion vertical as stated,
so as to first cause a sufficient movement of the Y frame to insure a closing of the
die-blocks and dies to grip and point the nail blanks and hold the blank until a
continued movement of the plunger forces the header outward to form the head;
these forms of the plunger and frame cause the frame to remain stationary until
the plunger has raised sufficiently to bring the vertical portion of its face past the
corresponding portion of the frame, and the inclined face of the plunger to act on
the frame. Obviously this necessitates the withdrawal of the hammer-stock slightly
in advance of the frame and to permit this advance movement, small spaces are left
between the hammer-stock and overlapping portions of the Y frame so as to permit
relative movement between these parts, and to hold the Y shaped frame stationary
during the first backward movement of the header block.
The gripping dies and pointing and cutting dies are confined in their carrying
blocks by cap-plates and screws securing said cap-plates. The pointing and cutting
off is performed at one operation by the same pair of dies and in order to provide
for the flow of metal demanded by the pointing of the nail and to compensate for
the resulting elongation of the blank, I mount the cutting and pointing dies in
recesses with their carrying blocks so that their working ends will be capable of an
outward movement longitudinally to the wire and I provide springs to press them
normally to the inward limit of their movement, in the direction of the feed.

page_text: When their ends are pressed together to form the point by a half cut and half
mash, the elongation produced by the flow of metal in the swaging operation forces
the meeting ends outward together, longitudinally to the wire and in opposition to
the pressure of the springs thus relieving the blank from violence and liability of
bending. This vibrating movement of the cutting and pointing dies has also the
very important functions of imparting a shear cut, causing the work to be done
with much less power, and of protecting the dies themselves from injury which is
liable to occur should they be forced directly together, end to end, without provision
for yielding. The necessity for frequent sharpening of the dies is thus obviated
and their durability greatly increased. The springs are confined within their
chambers by screws which are set forward as required to regulate their pressure.
In thus making cutting and pointing dies yielding, they are provided with convex
rounded steps upon which they rest by their concave ends. The position of the
step is such that when the die rests squarely thereon, it is against the inner or
forward wall of the recess, and it is held normally against this wall by means of
the spring, sufficient space being left in said recess to permit the die to yield
outwardly on compressing said spring.
To compensate for wear in both the gripping dies and the cutting and pointing
dies, and to keep them accurately up to their work I provide adjustable rear
bearings alike for both said sets of dies, consisting of wedges which are forced down
as required by set screws, clamp-nuts being employed to fix the adjusting wedges
in any position in which they are set. The adjusting wedges for the cutting and
pointing dies are inserted behind the rounded steps.
The nail or such like expeller may consist of any suitable means for releasing
the nail from the die. I prefer to employ a notched guide extending down to such
position that the wire is fed through its notch and which will hold the nail
centrally, so that when the dies open they necessarily withdraw from the nail or
such like article and release the latter, so that the nail is free to fall into the chute
or receptacle provided to receive it. This expeller is attached to a fixed portion
of the machine and its notched end is held rigidly in the line of feed, between the
cutting dies and gripping die so that the wire passes through the notch.
The feeding of the wire is effected by an oscillating dog formed on its sole with
teeth and pivotted on trunnions having bearings in a feed block which slides in
horizontal bearings and has a toothed base-plate. Between the plate and the
toothed feed dog the wire is gripped. A spring is provided to press the heel of the
feed dog upward and hold its toothed face normally in contact with the wire.
The feed dog is formed with a bore or socket, in which is mounted a gripping bar
carrying the teeth or serrations at its lower edge and rendered adjustable by an
adjusting screw at top. It is held in any position to which it may be adjusted
by a set screw. The lower serrated end constitutes the gripping medium of the
upper jaws or dog of the feeder. This dog rocks in a slot or groove in the feed
block and across the ends of this slot or groove are stops. The dog is further
provided with front and rear extensions which engage with said stops and limit the
rocking movement of the dog.
The aperture of the feed and consequently the feeding of the wire, is effected by
a series of annular or vertical shafts upon which are keyed pinions gearing with an
annular rack or cogged rim causing the vertical shafts to rotate in unison. The
annular rack is driven by a horizontal pinion on the upper end of a short vertical
shaft which carries at its lower end a horizontal bevelled gear wheel meshing with
the vertical gear wheel upon the main drive shaft. Upon the head of each vertical
feed shaft is a disc upon the top of which is fitted a flanged disc and which, when
the feed movement is connected, is compelled to rotate with the disc forced outward
by means of a clutch bolt on the disc forced outward by a spring into engagement
with a socket in the downwardly projecting flange of the disc. From the disc
connection is made with the sliding feed by a rod connected to said feed through
the medium of the feed dog and to the disc by means of a slide block working in a
dove-tail slot extending diametrically across the upper face of the disc said slide

page_text: block carrying a wrist-pin on which is a brass bushing interposed between said
wrist-pin and the eye of the connecting rod. The upper end of the wrist-pin
terminates in a screw stud having a nut which, when screwed down upon the
bushing tightly clamps the slide the bushing being for this purpose made a little
longer than the eye of the connecting rod so as to allow the latter to turn freely
upon the eccentric wrist formed by the pin and its surrounding bushing. When
the bushing is freed by turning back the nut the slide may be moved radially in its
dove-tail slot. This radial adjustment of the slide carrying the wrist-pin is to
regulate the length of the feed, may be effected by means of a horizontal screw
which works in a screw-socket tapped in the slide and is held against longitudinal
movement by collars on said screw, bearing against shoulders in the disc. In order
to rotate the adjusting screw to move the slide radially in and out, the said screw is
squared at either end for the reception of a wrench or key. The slide and wrist-
pin being adjusted as required to the operative distance, they are fixed in this
position by turning down the nut so as to clamp the bushing and the dove-tail slot
as already described.
The outer end of the connecting rod is formed of a hemispherical socket to fit
over the spherical head of the feed dog and is confined on said spherical head by
means of an externally threaded nut screwed into a threaded socket in the under
face of the end of the connecting rod, and having a spherical inner surface
corresponding with that of the spherical head upon which it works. A universal
joint movement is thus provided between the end of the connecting rod and the
reciprocating feed dog so as to permit the angular movement of the connecting rod
imparted by the wrist-pin and also the oscillating movement of the feed-dog. As
above described, the feed dog is mounted upon pivots so as to rock, and since the
reciprocating movement is communicated to the feed through the medium of said
log, it will be seen that as the feed is forced outward the dog raises and the feed
slides freely over the wire in its outward movement, but when the feed is drawn
inward, the dog grips the wire and it is fed inward to the required extent.
I provide for disconnecting the feed mechanism at the same time that any section
of the machine is thrown out by the operation of the coupling and uncoupling handle
through the medium of a cam underneath said lever which acts upon a dog pivotted
and passing beneath the flange of the disc so as to expel the spring clutch-bolt from
said flange and prevent its engagement therein.
The effect of this is to permit the inner or lower disc to turn freely and con-
tinuously beneath the disc without imparting any rotation to the latter and hence
without acting upon the feed mechanism.
Located upon the outer end of each section are a number of co-acting guide and
straightening rolls which are mounted in upper and lower blocks and arranged to
be separated for the introduction of the wire by an eccentric shaft controlled by a
hand lever. I mount upon the upper straightener block, a fixed nipping jaw and
an upper movable nipping jaw held normally elevated by a spring which carries it.
The upper nipping jaw is connected by a link with the eccentric shaft. The
nippers as well as the opening and closing of the straightening rolls are therefore
under control of hand lever.
Just outside of the train straightening rolls in each section, I mount a grooved
guide roll supported in a frame having flaring jaws which direct the wire into the
groove of roll and by this means the wire is eased and guided into the straightener.
In order to prevent the wire being drawn back as the feeder recedes, I provide
just behind or outside of the straightening rolls, a friction block, forced downward
by a spring against an adjustable friction block screw-threaded in the straightener
frame. The upper spring-pressed block is engaged by the upper roll block so that
said friction block and roller-block are both raised by the eccentric shaft in the act
of separating the rolls but are again lowered after the wire is inserted and permitted
to grip the wire with sufficient force to hold it against any tendency to be moved
by any means except the forward movement of the feeder, as intended.
The wire reei rests by its journals in bearings in brackets on the main frame. To

page_text: the said brackets are fulcrummed skid-levers in suitable position to receive the
journals as the loaded reel is rolled between said levers, after which by raising the
levers, the reel is deposited in its bearings, with great ease.
In a machine I have constructed I employ 10 of these radially-arranged nail-
forming mechanisms, but I may arrange a greater or less number of such
mechanisms, which when in connection with the operating mechanisms, are
actuated simultaneously, forming so many continuously operating nail or such like
machines which may be used for making nails or such like articles of as many
different sizes as desired by the regulation of the length of the feed movement of
each and adjusting the dies &c., to correspond. Or if desired any of the mechanisms
may be thrown out of gear by raising the hand lever so as to throw back the
-connecting links and separate the grip from the operating wedge.
The following is a description of the operation of the machine.
As the wedge plunger moves up, the inclined inner faces of the flanges of the
wedge-shoes engage the undersides of the inclined lips of the clutches and the latter
are drawn inward. This imparts an inward movement to the hammer-stock which
at first is independent of the Y shaped frames of the transmitting wedge frame
because the slot in the stem of the frame is longer than the post of the hammer-
stock, but after the lost or independent motion is completed, the continued upward
movement of the wedge-plunger causes all the parts to move together inwardly and
simultaneously, while this takes place the connecting rod begins to draw inward by
the feed-discs and this continues until the feed movement carries between the dies
sufficient length of wire to form a nail of the desired length before the completion
of the downward movement of the plunger, which imparts outward movement to
the Y shaped frame and the hammer stock causing the gripping and the pointing
and cutting dies to approach so as to grip and point and cut the nails by a single
movement, this done the dies rest in this position till the heading is completed, after
which the dies and hammer withdraw and the finished nail drops.
The working connections may be so timed that the feed has a practically
continuous reciprocation, the wire commencing to move forward as soon as the
finished, preceding nail is dropped by the dies, the forward movement being
completed just before the dies close, and the receding movement commencing just
after the dies have closed. The exact relation of the movements of these parts is
unimportant however, so long as the proper length of wire is fed in each time
before the dies come together.
Just before the plunger reaches the limit of its downward movement, .., when
the lower and upper ends of the vertical portions of the T wings and the Y shaped
frames come opposite, the latter will stop, the nails having been cut, pointed and
gripped. But while the Y shaped frames are not moving, the header will be given
a further outward movement by the inclines of the T wings acting on the inclines
of the blocks, thus causing the headers to torm the heads of the nails after they
have been gripped and pointed.
The inclines of the wedge-plunger and of the hammer-stock and the reciprocating
frame may be inverted should it be desired, and the machine will operate exactly
the same.
The machine is so devised that it may run either way as it has no
forward or backward movement, hence the shaft may be turned in either direction.
I would here remark that the machine as above described is principally
applicable to the manu:acture of nails but it is equally applicable to the manufacture
of screw blanks, rivets, bolt blanks, and other such articles, by variations in the
form and dimensions of the parts and when required by the omission of the pointing
and cutting off apparatus above described and the substitution theretor of dies
cutting square across the wire.
Dated this 29th day of January 1894
ROBERT POWELL,
By Harris & Mills,
23, Southampton Buildings, Londou, W.C., Agents.

page_text: Improvements in Machinery for the Manufacture of Nails, Screw-
Blanks, Rivets, Bolt Blanks, and such like Articles.
I, ROBERT POWELL, of 5 Euclid Avenue, Cleveland, Ohio, in the United
States of America, Mechanical Engineer, do hereby declare the nature of this
invention, and in what manner the same is to be performed, to be particularly
described and ascertained in and by the following statement :-
My invention relates to an improved system of wire nail and such like
machines in which several complete and independent sections or nail or such
like forming mechanisins are assembled or arranged in a smail area and operated
from a single source of power through the medium of mechanism hereinafter
described.
My invention consists broadly of the employment of a central source of power,
and a number of transmitting members, radiating from and actuated by the central
member and adapted to actuate any form of mechanism suitably arranged in
connection therewith.
My invention further consists in a machine of the character named, constructed
with a number of sections (each section constituting an operative machine in
itself) radiating from a common center and so located as to be operated simul-
taneously by the series of transmitting members which radiate from a central.
source.
In my machine the central power mechanism consists preferably of a main
vertically reciprocating actuating wedge, and power is communicated from this
main wedge through a series of radially reciprocating transmitting wedges to the
mechanisins to be actuated.
The nail or such like forming dies are operated by the transmitting wedges, and
the other details in the operation are provided for as well as means for throwing
out of action any one or more sections, while the remaining ones are kept in.
operation, as will hereinafter be described.
It will be observed that I have shown the main features of my machine
arranged for the manufacture of nails from a reel or spool of continuous wire, by
the use of new and improved dies, and guiding mechanism especially arranged for
conducting such material from which the nails are made, by such dies, but I desire
it to be understood that the parts of my machine, from which is obtained the
power which actuates the dies and some other parts, including the intermittent
feed, are quite as well adapted for forming bolt blanks, rivets, screw blanks, etc., etc.,
and I, therefore, do not limit myself to the use of the said dies nor to the
restricted application of the features which is illustrated in the drawings hereto
annexed, and described in the following description of said drawings. The
illustrated and described association of those features which are more or less
general in their application, is to be understood as simply employed to illustrate
the mode of operation of said features.
In the accompanying drawings forming part of this Specification-
Figure 1 is a plan of an entire machine, having ten independent sections, each
of which is a complete mechanism in itself and all of which are operated from a
single source of power.
Figure 2 is a central section through the machine, shown in Figure 1, in the
vertical plane of the power shaft.
Figure 24 is a transverse section through the crank of the power shaft,
showing in elevation the yoke for connecting the crank to the plunger, and the
bearings of said yoke.
Figure 2B is a plan of the parts shown in Figure 2^.

page_text: Figure 3 is a plan on an enlarged scale of one of the complete mechanisms
shown in Figure 1.
Figure 4 is a vertical central section of Figure 3, the lower driving connections
being omitted.
Figure 44 is an enlarged detail view of a portion of Figure 4.
Figure 5 is an end view of one of the separate mechanisms.
Figure 6 is a plan of the die blocks and dies mounted thereon.
Figure 7 is a side elevation of the inner face of one of the die blocks and parts
mounted thereon.
Figures 7 and 8 are respectively a top and a side view of one of the radial
Y-shaped power-transmitting frames.
Figures 9 and 10 are respectively a side and a top view of the hammer stock.
Figure 11 is a sectional view of a portion of Figure 4, showing, on an enlarged
scale, one of the couplings, by means of which the mechanisms are thrown into
and out of operative connection with the central plunger.
Figures 12 and 13 are sectional views, taken respectively on the line 12-12
and line 13-13, of Figures 7 to 10 and 14 and 15, and showing the relative
positions of the hammer-stock, side grips of the coupling, and Y-shaped frame
and the manner of securing them together and to the bed plate.
Figure 14 is an inside elevation of one of the side grips of the coupling.
Figure 15 is a plan of the pair of grips.
Figure 16 is a detail view of the annular rack and bevel gearing which establish
working connection between the main power shaft and the individual feed actuating
shafts.
Figure 17 is an elevation illustrating the connection between the annular rack
and the respective feeds.
Figures 18 and 19 are respectively a plan and side elevation of a crank-disk and
clutch which surmount each feed shaft.
Figure 20 is a sectional view of the feed clutch, and the cam on the coupling
link which throws out said clutch.
Figure 21 is a side view of the cam on said link, and
Figure 22 is a detail view of the annular flange on the under side of the crank
disk, which forms part of the clutch.
The central source of power consists of a plunger 2, which is hollow to secure
strength without unnecessary weight and is provided with a swell or bulge 2a.
Radiating from the swell 2a are wedge-ribs 2b, and between these wedge-ribs
the surface of the swell may be vertical as shown. A portion of the upper outer
face of each wedge-rib 26 is vertical, but, from said vertical portion the face of
each rib is inclined inwardly and downwardly, to provide a wedging face. On
each side of each rib, are formed flanges 2c, that are flush with or conform to the
outer faces of the rib, which are formed as just described. The parts 26 and 2c
hence constitute what I will term hereinafter wedging "T-wings." The inclined
outer faces of the T-wings act as wedges, the vertical portion serving to permit
lost motion, and the inner sides of the flanges thereof act similarly, but in the
opposite direction, the outer faces acting radially outward, and the inner faces
acting radially inward, as will now be described. These wings may be formed
integral with the plunger, but I prefer to form them separately and attach them as
shown, with the bolts 2d, as by so constructing them, they can be made of more
suitable material and may be replaced at will.
The plunger 2 is guided in upper box 3, supported by legs 3a, and lower box 4,
in bed 1, and receives a vertical reciprocating movement from a crank shaft 5
working in a yoke 6 attached to the plunger or by other suitable means.
The yoke 6 has an opening 6a for the end of the plunger, which is squared to fit
said opening, and is secured therein by keys 66 between the yoke and plunger,
recessed into each. The parts are all secured in place by transverse bolts 6c. The
plunger 2 also has specially formed bearings at its lower end for guiding it vertically
as it is reciprocated by the crank. These bearings consist of grooves 6d, in which

page_text: work corresponding ribs 6e on the yoke. The ribs 6e have tongue and groove
connection 6f with the yoke 6, and this connection is made wedging for adjustment
and taking up wear, such adjustment being effected by screws 6g.
The yoke has a sliding journal-box 5a in which the crank of the main drive shaft
is journalled, and this journal-box has an adjusting wedge 56 moved by screw 5c for
taking up wear.
As any desirable number of sections or mechanisms are arranged equidistantly
in radial position on the bed 1 around the central plunger 2, which operates them
all simultaneously, and of these as many as desired may be placed in operative
connection, while the rest are thrown out, as will presently be explained, and, as
these radial machines are all alike, I will describe one of them with special reference
to Figures 3 to 22, and this description will suffice to disclose and elucidate the
construction and operation of the entire combined machine. For each radial
machine there is a Y-shaped transmitting frame or member 7 controlled at its inner
end by the central source of power as will be described, and having wedging
arms 7a, for operating the nail-forming dies 8, also with a hammer stock 9, which
also receives reciprocating movement from the central source or wedge-faced
plunger 2. The Y-shaped frame 7 and hammer stock 9 are forced radially outward
by each descent of the plunger 2, and as the plunger moves up the hammer stock 9
and through it the Y-frame 7 are drawn in. This inward movement of the parts is
transmitted through the medium of side grips 10 which engage behind T-wedges 26
and which are connected to the header-block 9, by a coupling 11 to be hereinafter
described, and which constitutes the means of throwing the whole section into and
out of operation. The extremities of the arms 7a of the Y-shaped frame 7 are
wedge-shaped and provided with flanged plates 76 engaging with the die-blocks 8,
so as to force them together on the wire in the outward movement of the Y-frame
and to draw them apart by the inward movement of said frame. The hammer stock 9
carries a post 9a projecting up through a slot 7c in the shank of the Y-frame 7
(see Figures 74 to 10), whereby the frame may be drawn in by the block, and this slot
is of sufficient length to permit lost or relative motion between the frame and block.
This lost or relative motion outward is produced by extending the operating face of
the plunger-shoe in a vertical plane, and providing a corresponding vertical face at
the lower part of the inner end of the frame 7, so that when the Y-shaped frame 7
completes its outward movement it is held in its extended position while the hammer
stock continues to be moved outward. The effect of these movements is to hold
the gripping dies 8 in their closed position on the blank, while the stock 9 performs
its work, after which, at the termination of the outward movement of said stock it
is moved inward through the medium of grips 10 till the post 9a strikes the inner
end of slot 7c, after which the stock 9 and frame 7 move inward together, thus
opening the dies and releasing the finished nail.
The inner end of the Y-frame 7 is provided with a brass face 7d to take the
wear, said brass face being set in a dove-tail as shown, so as to be easily replaced.
A similar brass piece 96 is provided on the inner end of the hammer stock 9, which
receives its radial reciprocating movement from the lower wedge face of the plunger
shoe in the same way in which the Y-frame receives reciprocating movement from
the upper wedge face. The parts are suitably formed and arranged to
simultaneously grip, cut and point, and then to head the blank by a substantially
continuous movement of the frame and hammer stock. Between the hammer
stock 9 and the hammer 9c, operated thereby, is a wedge 9d adjusted by a screw 9e
so as to accurately set up the hammer to compensate for wear and adapt it to operate
effectively in heading the nail (see Figure 4).
As will be seen in Figures 12 and 13 the hammer stock 9 is adapted to
reciprocate in a suitable way or guide 9f on the bed-plate 1. This stock 9 is
formed with laterally projecting ribs 99, upon which are mounted side grips 10
which slide on said central section of the hammer stock. The inner ends of these
sliding side grips 10 are provided with lips 10a inclined to correspond to, and
engaging behind the inner faces of the T-Hanges 2c of the plunger rib or shoe 26,
B

page_text: with which they engage. The inner end of the stock 9 (sec Figures 9 and 10) is
inclined at 9h and is parallel with the outer face of its opposing T-wing 26 with
which it engages. The outer end of the stock 9 is formed with a recess 9i to receive
the hammer or header 9c. The Y-frame 7 and hammer stock 9 are held together,
but so as to allow relative movement, by standard arms 106 on the side grips 10,
extending upward and meeting above the stem of the Y-shaped frame and stock 9.
and behind the post 9a and securing said frame and hammer-stock together. At
the same time the stock 9 is secured to the bed-plate by guides so that all the parts
are held down.
The coupling 11 consists of side links ila swiveled at 116 to arms 10%, and has a
handle 11e trunnioned at 11d, said handle being formed to engage at 1le on the
post 9a of the hammer stock (see Figures 3, 4, and 11).
It will be understood that the handle 11c of coupling 11, with the attachments
described, form the connection between the hammer-stock which receives the
outward pressure of the wedge surfaces in the downward movement of the plunger 2
and the grip 10 by which the parts are drawn inward on the upward stroke of the
plunger. 11 is a bearing plate, upon a screw rod 11g, which is mounted axially
in the handle 11c, and adjustable through the medium of a nut 11h.
adjustment of the bearing plate 11f by the screw rod 11 takes up lost motion
produced by wear between the operating flanges of the plunger and the bearing-
faces of the hammer-stock and grip on which they act.
The
In order to throw any one of the radial machines out of gear, it is only necessary
to throw up the gravitating handle 11c, which movement, acting through the
links 11a, throws the retracting flanges of the grip 10 inward beyond the reach
of the operating flanges 2c of the plunger-shoe 26, and thereby all the parts of this
particular machine or section are left at rest.
The wedging arms 7a of the Y-shaped frame have secured to them, so as to
project inwardly over their edges, plates 7d, oblique or inclined inwardly from their
outer ends, parallel with the inclined inner edges of said limbs, and these flanges
are received by correspondingly inclined grooves 8a in the die-blocks 8, which also
have inclined or oblique edges parallel with the grooves 8a, engaged by the inclined
or oblique edges of said arms 7a. By means of this construction, when the Y-shaped
frame is reciprocated longitudinally by the inclined end of its stem, that is paralle!
with the inclined face of the opposing plunger shoe, the dies of this particular set
will be caused to approach and recede from each other, and perform their functions,
the dies being forced together by the engagement of the oblique edges of the
die-blocks and the oblique edges of the arms 7a, and being drawn apart by the
oblique flanges 7e working in the oblique grooves in the die blocks. The stem of
the frame has a portion of its face inclined and a portion vertical as stated, so as
to first cause a sufficient movement of the Y-frame to ensure a closing of the
die-blocks and dies to grip and point the nail blanks and hold the blank until a
continued movement of the plunger forces the header outward to form the head;
forming the plunger and frame in this manner causes the frame to remain stationary
until the plunger has raised sufficiently to bring the vertical portion of its face
past the corresponding portion of the frame, and the inclined face of the plunger
acts on the frame. Obviously this necessitates the withdrawal of the hammer-
stock slightly in advance of the frame, and to permit this advance movement, small
spaces are left between the hammer-stock and overlapping portions of the Y-frame
so as to permit relative movement between these parts.
The gripping dies 12, and pointing and cutting dies 13 are confined in their
carrying blocks 8, by cap-plates 86 and screws 8c securing said cap-plates. (See
Figures 6 and 7.) The pointing and cutting off is performed at one operation by
the same pair of dies 13, and in order to provide for the flow of metal demanded
by the pointing of the nail and to compensate for the resulting elongation of the
blank, mount the cutting and pointing dies 13 in recesses in their carrying
blocks 8 so that their working ends will be capable of an outward movement
longitudinally to the wire, and I provide springs 13a to press them normally to the

page_text: inward limit of their movement, in the direction of the feed. When their ends
are pressed together to form the point by a half cut and half mash, the elongation
produced by the flow of metal in the swaging operation forces the meeting ends
outward together, longitudinally to the wire and in opposition to the pressure of
the springs 13a, thus relieving the blank from violence and liability of bending.
This vibrating movement. of the cutting and pointing dies has also the very
important functions of imparting a shear cut, causing the work to be done with
much less power, and of protecting the dies themselves from injury which is liable
to occur, should they be forced directly together, end to end, without provision
for yielding. The necessity for frequent sharpening of the dies is thus obviated
and their durability greatly increased. The springs are confined within their
chambers by screws 13c which are set forward as required to regulate their
pressure.
In order to thus make the cutting and pointing dies yielding, they are provided
with convex rounded steps 13d upon which they rest by their concave ends 13e.
The position of the step is such that when the die rests squarely thereon, it is
against the inner or forward wall of the recess, and it is held normally against this
wall by means of the spring 13c, sufficient space being left in said recess to permit
the die to yield outwardly on compressing said spring.
are
To compensate for wear in both the gripping dies and the cutting and pointing
dies, and to keep them accurately up to their work I provide adjustable rear
bearings alike for both said sets of dies, consisting of wedges 8c which
forced down as required by set screws 8d, clamp-nuts 8e being employed to fix the
adjusting wedges in any position in which they are set. The adjusting wedges for
the cutting and pointing dies are inserted behind the rounded steps 13d, as shown.
The nail expeller may consist of any suitable means for releasing the nail from
the die. I prefer to employ a notched guide 14 (see Figure 4), extending down to
such position that the wire is fed through its notch 14a, and which will hold the
nail centrally, so that when the dies open they necessarily withdraw from the nail
and release the latter, so that the nail is free to fall into the chute or receptacle
provided to receive it. This expeller 14 is attached to a fixed portion of the
machine at 146, and its notched end 14a is held rigidly in the line of feed, between
the cutting dies 13 and gripping dies 12, so that the wire passes through the
notch 14a.
The feeding of the wire is effected by an oscillating dog 15 formed on its sole with
teeth 15a and pivoted on trunnions 156, having bearings in a feed block 15c, which slides
in horizontal bearings 15d and has a toothed base-plate 15e. Between the plate 15e and
the toothed feed dog 15 the wire R is gripped. A spring may be provided to press
the heel of the feed dog upward and hold its toothed face normally in contact with
the wire. The feed dog is formed with a bore or socket, in which is mounted a
gripping bar 15f carrying the teeth or serrations 15a at its lower edge and rendered
adjustable by an adjusting screw 15g at top. It is held in any position to which it
may be adjusted by a set screw 15h. The lower serrated end 15a constitutes the
gripping medium of the upper jaw or dog of the feeder. This dog rocks in a slot
or groove 15 in the feed block 15c, and across the ends of this slot or groove are
stops 15k. The dog is further provided with front and rear extensions 15m, which
engage with said stops 15k and limit the rocking movement of the dog.
The operation of the feed and consequently the feeding of the wire, is effected
by a series of vertical shafts 16 (sce Figures 16 to 22) upon which are keyed
pinions 16a gearing with an annular rack or cogged rim 17, causing the vertical
shafts to rotate in unison. The annular rack 17 is driven by a horizontal pinion 18.
on the upper end of a short vertical shaft 18a, which carries at its lower end a
horizontal beveled gear wheel 186 meshing with the vertical gear wheel 5d upon
the main drive shaft 5. Upon the head of each vertical feed shaft 16 is a disk 19,
upon the top of which is fitted a flanged disk 19a and which, when the feed
movement is connected, is compelled to rotate with the disk 19 by means of a
clutch bolt 156 on the disk 19 forced outward by a spring 19c into engagement

page_text: with a socket 19d in the downwardly projecting flange of the disk 19a. From the
disk 19a connection is made with the sliding feed by a rod 20 (see Figure 4),
which rod is connected to the disk 19a by means of a slide block 20a working in
a dove-tail slot 206 extending diametrically across the upper face of the disk 19a,
said slide block carrying a wrist-pin 20c on which is a brass bushing 20d interposed
between said wrist-pin and the eye of the connecting rod 20. The upper end of the
wrist-pin 20c terminates in a screw stud 20e having a nut 20f which, when screwed
down upon the bushing 20d, tightly clamps the slide 20u, the bushing being for this
purpose made a little longer than the eye of the connecting rod so as to allow the
latter to turn freely upon the eccentric wrist formed by the pin 20c and its
surrounding bushing. When the bushing is freed by turning back the nut 20f the
slide 20a may be moved radially in its dove-tail slot. This radial adjustment of
the slide carrying the wrist-pin is to regulate the length of the feed, and it may
be effected by means of a horizontal screw 20g which works in a screw-socket
tapped in the slide 20a and is held against longitudinal movement by collars 201
on said screw, bearing against shoulders 20k in the disk. In order to rotate the
adjusting screw to move the slide radially in and out, the said screw is squared at
either end for the reception of a wrench or key. The slide and wrist-pin being
adjusted as required to the operative distance, they are fixed in this position by
turning down the nut so as to clamp the bushing and the dove-tail slot as already
described.
The outer end 21 (see Figure 4) of the connecting rod 20 is formed of a
hemispherical socket 21a to fit over the spherical head 216 of the feed dog 15,
and is confined on said spherical head by means of an externally threaded lower
nut 21c screwed into a threaded socket in the under face of the end of the
connecting rod, and having a spherical inner surface corresponding with that of
the spherical head 216 upon which it works. A universal joint movement is thus
provided between the end of the connecting rod and the reciprocating feed dog so
as to permit the angular movement of the connecting rod imparted by the wrist-
pin 20c and also the oscillating movement of the feed dog 15. As above described
the feed dog 15 is mounted upon pivots so as to rock, and since the reciprocating
movement is communicated to the feed through the medium of said dog, it will be
seen that as the feed is forced outward the dog raises and the feed slides freely over
the wire in its outward movement, but when the feed is drawn inward, the dog grips
the wire and it is fed inward to the required extent.
I provide for disconnecting the feed mechanism at the same time that any section
of the machine is thrown out by the operation of the coupling and uncoupling
handle 11c, through the medium of a cam 22 underneath said handle which acts upon
a dog 22a pivoted at 226 and passing beneath the flange of the disk 19a, so as to
expel the spring clutch-bolt 196 from said flange and prevent its engagement therein.
The effect of this is to permit the inner or lower disk 19 to turn freely and continuously
beneath the disk 19a without imparting any rotation to the latter and hence without
acting upon the feed mechanism.
Located upon the outer end of each section (see Figures 3 and 4) are a number
of co-acting guide and straightening rolls 23, 23a which are mounted in upper and
lower blocks 236, 23c and arranged to be separated for the introduction of the wire
by an eccentric shaft 23d controlled by a hand lever 23e. The rolls 23, 23a are
made adjustable by set screws 23f. I mount upon the upper straightener block 236
a fixed nipping jaw 24 and an upper movable nipping jaw 24a, held normally
elevated by a spring 246 which carries it. The upper nipping jaw 24a is
connected by a link 24c with the eccentric shaft 23d. The nippers as well as
the opening and closing of the straightening rolls are, therefore, under control of
hand lever 23e.
Just outside of the train of straightening rolls in each section I mount a grooved
guide roll 25 supported in a frame 25a having flaring jaws 256, which direct the wire
into the groove of roll 25, and by this means the wire is eased and guided into the
straightener.

page_text: In order to prevent the wire being drawn back as the feeder recedes I provide
just behind or outside of the straightening rolls an upper friction block 26, forced
downward by a spring 26a against an adjustable lower friction block 266, screw-
threaded in the straightener frame. The upper spring-pressed block 26 is carried by
the upper roll-block 236 so that said friction block is raised with the roller-block
by the eccentric shaft 23d in the act of separating the rolls, but is again lowered
after the wire is inserted and permitted to grip the wire with sufficient force to hold
it against any tendency to be moved by any means except the forward movement of
the feeder, as intended.
As will be seen from Figures 2 and 5, the wire reel 27 rests by its journals 27a in
brackets 28 on the main frame. To the said brackets 28 are fulcrumed skid-
levers 29 in suitable position to receive the journals 27a as the loaded reel is rolled
between said levers, after which, by raising the levers, the reel is deposited in its
bearings, with great ease.
In my present illustration I have shown 10 of these radially-arranged nail-forming
mechanisms, but I may arrange a greater or less number of such mechanisms, which,
when in connection with the operating mechanisms, are actuated simultaneously,
forming so many continuously operating nail machines which may be used for
making nails of as many different sizes as desired by the regulation of the length
of the feed movement of each and adjusting the dies, etc., to correspond. Or if
desired, any of the mechanisms may be thrown out of gear by raising the hand
lever 11c so as to throw back the connecting links and separate the grip from the
operating wedge.
OPERATION.
As the wedge plunger moves up, the inclined inner faces of the flanges 2c of the
wedge-shoes 26 engage the undersides of the inclined lips 10a of the clutches 10 and
the latter are drawn inward. These impart an inward movement to the hammer-
stocks 9, which movement is at first independent of the Y-shaped transmitting
frames 7, because the slots in the stems of the said frames are longer than the
posts of the hammer-stocks, but which, after the lost or independent motion is
completed is imparted likewise to the Y-shaped frames, and both parts then move
together inwardly and simultaneously; while this takes place the connecting rods 20
begin to be drawn inward by the feed-disks 19a, and this continues and the feed
movement carries between each pair of dies sufficient lengths of wire to form nails
of the desired length, before the completion of the downward movement of the
plunger, which imparts outward movement to the Y-shaped frames and the hammer-
stocks, and causes the gripping and the pointing and cutting dies to approach so as
This done the dies rest
to grip and point and cut the nails by a single movement.
in this position till the heading is completed, after which the dies and hammer
withdraw and the finished nail drops.
The working connections may be so timed that the feeds have a practically
continuous reciprocation, the wire commencing to move forward as soon as the
finished preceding nails are dropped by the dies, the forward movement being
completed just before the dies close, and the receding movement commencing just
5 after the dies have closed. The exact relation of the movements of these parts
is unimportant, however, so long as the proper length of wire is fed in, each time,
before the dies come together.
Just before the plunger reaches the limit of its downward movement, i.e., when
the lower and upper ends of the vertical portions of the T-wings and the Y-shaped
0 frames come opposite, the latter will stop, the nails having been cut, pointed and
gripped. But while the Y-shaped frames are not moving, the headers will be given
a further outward movement by the inclines of the T-wings acting on the inclines
of the header blocks, thus causing the headers to form the heads of the nails after
they have been gripped and pointed.
5
The inclines of the wedge-plunger and of the hammer-stocks and the reciprocating
frames may be inverted should it be desired, and the machine will operate exactly

page_text: Having thus ascertained the nature of my said invention, and in what manner
the same is to be performed, I declare that what. I claim is-
1. In a nail or other like machine, the herein-described means for transmitting
power, consisting of a vertically reciprocating main actuating member, and a
symmetrical series of transmitting members radiating from and actuated by said
central member, substantially as and for the purposes set forth.
2. In a nail or other like machine, as a means for transmitting power, the com-
bination of the central reciprocating main actuating member and the series of
reciprocating transmitting members projecting at an angle from the main member
and having working connections whereby they receive reciprocating movement
therefrom, substantially as set forth.
3. In a nail or other like machine, as a means of transmitting power, the com-
bination of a central main reciprocating wedge, and a series of transmitting members
symmetrically radiating from said central wedge and having connection therewith
whereby they are forced out and drawn inward radially as the central wedge
reciprocates, substantially as and for the purpose set forth.
4. In a nail or other like machine, the combination of a central reciprocating
wedge and a symmetrical series of radiating transmitting members receiving
reciprocatory movement from the main wedge, and having wedging faces for
performing work in substantially the manner explained.
5. In a nail or other like machine the combination of a main central member
having a number of circumferential flanged wedges and a series of transmitting
members engaged at their inner ends by the flanged wedges on the main member
and receiving reciprocating movement therefrom and having at their outer ends
means for performing work, substantially as set forth.
6. In a machine of substantially the character specified the combination of a
central actuating wedge and a series of forming mechanisms radiating from and
actuated by said central wedge, substantially in the manner and for the purpose set
forth.
7. In a machine of substantially the character specified the combination of a
series of radially arranged and radially feeding forming mechanisms and the
common central power operating thereon, substantially in the manner explained.
8. A nail or other like machine consisting of a number of forming mechanisms, a
motor common to all and means for disconnecting at will one or more of said
mechanisms from the motor, substantially as set forth.
9. A nail machine consisting of a number of radially arranged nail-forming
mechanisms, a common actuating device and means for disconnecting one or more
of said nail-forming mechanisms from the actuating device, substantially as set
forth.
10. A nail machine consisting of a centrally arranged reciprocating wedge and a
symmetrical series of radiating nail mechanisms having actuating connection with
said wedge, as explained.
11. In a nail machine, the combination of a main reciprocating wedge, a series
of reciprocating transmitting wedges receiving motion from the main wedge,
and nail forming mechanisms operated by said transmitting wedges as explained.
12. A multiplex nail machine constructed substantially as herein described, of a
series of complete nail-forming mechanisms, a vertically reciprocating wedge plunger,
from which each complete nail-forming mechanism of the series radiates, and
connecting mechanisms operated by said plunger whereby the various working
elements of each nail-forming mechanism are actuated, substantially as set forth.
13. The combination of a series of nail-forming mechanisms arranged radially {

page_text: around a common centre, the vertically moving central plunger 2 and the removable
plunger shoes 26 imparting radial movement to the operating parts from the vertical
movement of the plunger, as explained.
14. The combination of the vertically moving wedge plunger, the radially moving
die operating frame, the header-block and the removable brasses or bearing plates,
for taking the wear between the plunger wedges and the radially moving parts, as
explained.
15. The combination of the vertically moving wedge-plunger, the radially moving
header-block, and the interposed wedge, for adjusting the stroke and taking up the
wear of the header, as explained.
16. The combination of the vertically moving wedge-plunger, the radially moving
header block, the header, the wedge and the adjusting screw 18, substantially as
and for the purpose set forth.
17. In a nail machine, the combination of a reciprocating frame carrying inclined
flanges, and die-carrying blocks having grooves corresponding with the incline of
the flanges to receive the same, substantially as set forth.
18. In a nail machine, the combination of a vertically reciprocating wedge-
plunger, a reciprocating frame operated thereby, the die-carrying blocks and dies
having connection with said frame, substantially as set forth.
19. In a nail machine, the combination of a reciprocating Y-shaped frame,
means for reciprocating it from its stem end, the die-carrying blocks and dies, and
means at the limbs of the frame provided with inclined portions for operating the
dies substantially as set forth.
20. In a nail machine the combination of the reciprocating die-block having the
inclined bearing face, and the wedging transmitting plunger engaging said face for
forcing the block inward, one of said parts also having an inclined groove, and the
other a flanged plate engaging said groove for drawing the block outward,
substantially as set forth.
21. In a nail machine, the combination of a reciprocating Y-shaped frame,
means for reciprocating it from its stem end, plates fixed to the limbs of the frame
and provided with inclined flanges, the dies, and the die-carrying blocks having
grooves to receive said flanges and corresponding to their inclination, substantially
as set forth.
22. In a nail machine, the combination of a reciprocating frame, the dies
operated thereby, the reciprocating header block and header adapted to reciprocate
with and having a slight relative movement to said frame, and means for
reciprocating said devices, substantially as set forth.
23. In a nail machine, the combination of a reciprocating frame having a slot,
the dies operated by the frame, a reciprocating header block and header, the
former having a projection received by but shorter than said slot to permit
relative movement of the header block, means for confining the reciprocating
frame in its proper rectilinear movement and means for operating said devices,
substantially as set forth.
24. In a nail machine, having gripping, pointing and cutting devices, the
combination of a reciprocating frame for operating the gripping, pointing and
cutting devices, a header block and header movable relatively thereto, said frame
and header block having inclined ends for forcing the frame and header outwardly,
and means for drawing them inwardly, substantially as set forth.
25. In a nail machine, having gripping, pointing and cutting devices, the
combination of a reciprocating frame for operating the gripping, pointing and
cutting devices, header block and header movable relatively thereto, said frame
having an end with an inclined and a vertical face, and said header block having
an inclined end, means for engaging the inclined portions of said devices, and the
vertical portion of said frame, whereby they are forced outwardly, and means for
drawing them inwardly, substantially as set forth.
26. In a nail machine, having gripping, pointing and cutting devices, the
combination of a reciprocating frame for operating the gripping, pointing and

page_text: cutting devices, and having an end with a portion inclined and a portion vertical,
a header block having an inclined end and movable relatively to the frame, a
header carried thereby, and a reciprocating plunger, having inclined and vertical
portions on its exterior for engaging the corresponding portions of the frame and
header block for forcing them outwardly, and means for drawing them inwardly,
substantially as set forth.
27. In a nail machine, having gripping, pointing and cutting devices, the
combination of a reciprocating frame for operating the gripping, pointing and
cutting devices, and having an end with inclined and vertical portions, a header
block having an inclined end and movable relatively to the frame, a header carried
thereby, and a reciprocating plunger provided with wings, the outer faces of which
have inclined and vertical portions for engaging the reciprocating portions of the
frame, and hammer-stocks for forcing them outwardly, and means for drawing them
inwardly, substantially as set forth.
28. In a nail machine having gripping, pointing and cutting devices, the
combination of a reciprocating frame for operating the gripping, pointing and
cutting devices, and having an end with inclined and vertical portions, a hammer-
stock having an inclined end and movable relatively to the frame, a header carried
thereby, gripping lips of the hammer-stock projecting on each side of and beyond
its inclined end, and a reciprocating plunger provided with T-wings, the outer faces
of which have inclined and vertical portions for engaging the corresponding portions
of the frame and header block and the inner sides of the flanges of the wings
being engaged by the gripping lips of the hammer-stock, substantially as and for
the purpose set forth.
29. In a nail.machine, the combination of a header block carrying a header and
provided with gripping lips, and a plunger provided with a T-wing having an
inclined face, said header block having an inclined end engaged by the incline of
the T-wing, being inclined and engaged by said gripping lips, substantially as and
for the purposes set forth.
30. The herein-described wedge-shaped plunger, in combination with nail-forming
mechanism, operated by said plunger, substantially as set forth.
31. In a nail machine, the herein-described plunger provided with wings having
faces extending from near one end of the plunger inwardly toward the other end,
substantially as set forth.
32. In a nail machine, the hercin-described plunger provided with T-wings with
inclined faces and correspondingly inclined on the inner sides of the flanges of said
wings, substantially as set forth.
33. In a nail machine the combination of the bed plate, the nail-forming device,
the transmitting wedge operating said forming device, and the bearing for said
transmitting wedge, attached to the bed plate supporting the transmitting wedge
laterally and adjustable to take up wear as explained.
34. In a nail machine the combination of the bed plate, the laterally reciprocating
dies, the wedging Y-shaped frame for reciprocating the dies, and the lateral
support for the Y-shaped frame, consisting of a wedge adjustably mounted on the
bed plate as explained.
35. In a nail machine the combination of a header-block carrying a header,
movable grips to said block provided with lips, means for moving said grips in and
out, and a reciprocating plunger having flanges for engaging said lips when in
their inner position and which are non-operative when the lips are in their outer
position, substantially as and for the purpose set forth.
36. In a nail machine the combination of a hammer-stock carrying a header,
grips movable relatively to said hammer-stock provided with lips for retracting
the same when the parts are locked together, a reciprocating wedge plunger having
flanges engaging the aforesaid lips for retracting the parts and a lever fulcrumed
in one member and connected by a link with the other so as to lock the parts
together when they are to be moved in and out by the motion of the plunger and
to release the grips when the parts are to be rendered inoperative.

page_text: 37. A multiple nail machine constructed substantially as herein described, with
a series of nail-forming mechanisms radiating from a common centre, a vertically
reciprocating wedge-plunger at said center, each of said mechanisms having its
own cutting, gripping and heading dies operated from said plunger, and an individual
disconnecting mechanism for each of said nail-forming mechanisms, whereby any
one or all of them may be thrown out of action, substantially as set forth.
38. A nail machine having a plunger, and upper and lower guides for said
plunger, the upper guide being provided with radiating or spreading arms for
holding it in position substantially as set forth.
39. In a nail machine the combination of the reciprocating plunger, having the
yoke on its lower end, the drive-shaft having a crank working in the yoke for
reciprocating the plunger, and the bearing for said lower end of the plunger,
consisting of the grooves on the machine frame, and the ribs on the yoke sliding in
said grooves, substantially as and for the purpose explained.
40. In a nail machine the combination of the frame, the reciprocating plunger,
having driving connections substantially as described, and the bearing for the end
of said plunger, consisting of the grooves on the frame and the wedging ribs
adjustably secured to said plunger and working in said grooves, for the purpose
explained.
41. In a nail machine the combination of the plunger, the ribs having adjustable
wedging tongue and groove connection with the plunger, and rounded bearing
faces, and the bearing frame having rounded grooves in which said ribs slide
substantially as and for the purpose set forth.
42. In a nail machine the combination of the vertically reciprocating plunger,
the drive shaft, and the connection between the plunger and shaft, consisting of the
yoke on the end of the plunger, the journal box sliding in the yoke and having
wedging adjustment to take up wear therein, and the crank on the shaft working
in said journal box substantially as explained.
43. In a nail machine the combination of the driving crank-shaft, the vertically
reciprocating plunger, the yoke in which the crank of said shaft works, having an
opening for receiving the end of the plunger, the keys between the overlapped
faces of the yoke and plunger, and recessed into each, and the transverse bolts for
holding the parts together, as explained.
44. The combination of the hammer-stock provided with a post or standard,
the movable grips extending above the hammer-stock, a flanged wedge-shaped
plunger for moving the combined hammer-stock and grips in and out by its recipro-
cating motion, the lever handle fulcrumed in the post, the links connecting the
handle to the standards and a bearing plate engaging with the post so as to lock
the hammer-stock and grips together or release them at the will of the operator as
explained.
45. The combination of the flanged wedge-shaped plunger, the hammer-stock
having a post, the movable flanged grips extending above the hammer-stock and
handle fulcrumed in the post, the links jointed to the handle and standards, the
bearing plate mounted in the handle and the screw rod for setting up the bearing
plate as required to take up slack and lost motion between the flanges of the
plunger and side pieces as explained.
46. In a machine of substantially the character specified, a reciprocating die,
constructed to yield in the direction at an angle to the line of reciprocation,
substantially as and for the purpose set forth.
47. A nail machine constructed with the backwardly yielding cutting dies,
substantially as described, and adapted to be restored automatically to normal
position, when released, as set forth.
48. In a nail machine the combination of a pair of die blocks with cavities of
greater horizontal width in the direction of the feed than the dies contained therein
and a pair of dies mounted movably in said cavities, having cutting faces acting
shearwise under the backward niovement of the working ends of the dies,
substantially as set forth.

page_text: 49. In a nail machine, the combination of a pair of die blocks, backwardly
moving cutting dies mounted therein and springs thrusting the working ends of the
dies forward in the direction of the feed, substantially as set forth.
50. The combination of the die blocks, the dies mounted therein with limited
play longitudinally to the rod, the springs tending to press the dies forward and
screws regulating the pressure of the springs as explained.
51. In a nail machine, the combination of a pair of die blocks, opposed dies
mounted therein, means for forcing together the opposed dies and drawing them
apart, and wedges interposed between the backs of the dies and the die blocks to
regulate the projection or approximation of the dies and compensate for the wear
of their faces as explained.
52. In a nail machine, a pair of die blocks, opposed dies mounted therein, means
for forcing the opposed dies together and drawing them apart, wedges interposed
between the backs of the dies and the die blocks to regulate the projection or
approximation of the dies and compensate for the wear of their faces and screws
for operating the said wedges, substantially as herein set forth.
53. The wire reel in combination with bearing brackets and skid levers
fulcrumed on said brackets for lifting the reel into its bearings, as explained.
54. A nail machine constructed with a radial series of feeding and nail forming
mechanisms and a concentric series of actuating devices consisting of vertical
shafts, means for communicating simultaneous rotation thereto and an eccentric
pin and rods on said shafts operating the feed mechanism, substantially as
described.
55. The combination of the gripping and heading dies arranged in an annular
series, central mechanism for operating the same, the main driving shaft, the
transmitting shait, bevel wheels connecting said shafts, the upper pinion on the
transmitting shaft, an annular rack receiving motion from said upper pinion and an
annular series of feed shafts receiving simultaneous rotation from said annular rack,
as and for the purpose explained.
56. The combination of the gripping and heading dies arranged in annular series,
the central mechanism for operating them, the annular series of feed shafts, means
for rotating the same, crank disks on said feed shafts, oscillating feed dogs and
connecting rods between the crank disks and feed dogs, substantially as and for the
purpose set forth.
'
57. In a nail machine, the combination of the reciprocating feed, consisting of
the lower plate, a co-operating rocking feed dog and a reciprocating connecting
rod connected to said feed dog, whereby the feed grips in one direction and releases
in the opposite direction, as explained.
58. In a nail machine, the combination of the nail-forming mechanism, having
means for actuating, a feed device having connection through the medium of a
clutch actuating means, a switch for throwing the nail forming mechanism out of
operation, and connection between said switch and clutch whereby the feed is
likewise stopped, as explained.
59. In a nail machine, the combination of nail-forming mechanism, having
means for actuating it and a switch controlling the connection with said actuating
means, a feed actuated through the medium of a clutch having a spring pressed
bolt for connecting the parts of a clutch, a movable dog for displacing said bolt,
and a cam on the switch for engaging said dog, substantially as and for the purpose
explained.
60. The combination of the feed shaft, the fixed disk thereon, the loose crank
disk, and the clutch device for connecting said disks, substantially as and for the
purposes set forth.
61. The combination of the radially arranged gripping and heading dies, central
operating mechanisms, detaching device for throwing the several gripping and
heading mechanisms out of gear, the feed disks, the clutch connecting said disks
and connections for disconnecting said feed disks in the act of detaching the
gripping dies, as explained.

page_text: 62. The combination of the feed shaft, the feed disk, the radially adjustable wrist
pin, and the screw mechanism for adjusting the same, substantially as set forth.
63. The combination of the feed shaft; the feed disk, the radially adjustable wrist
pin, the adjusting mechanism for said pin and the clamping device for fixing said
pin in its adjusted position, as explained.
64. The combination of the feed shaft 16, feed disk 19, connecting rod 20; feed
dog 15, and ball joint 21" 21" 21° connecting said rod and dog and permitting their
relative oscillating motion as explained.
65. The combination of the feed shaft 16, feed disk 19, connecting rod 20, feed
dog 15, spherical head 21°, spherical socket 21, and spherical faced nut 21° forming
a universal joint between said connecting rod and feed dog, substantially as and for
the purpose set forth.
66. In a feed for nail machines, the combination of the sliding feed-blocks slotted.
as shown, the rocking dog mounted in the slot and the stops at the ends of said slot
for limiting the rocking of the dog as explained.
67. In a feed for nail machines, the feed dog, having a gripping surface and
trunnioned as described to cause said surface to grip the material to be fed, as
explained.
68. In a feed for nail machines the trunnioned dog, operating substantially as
described, and having the front and rear extensions for limiting its rocking on its
trunnions as explained.
.
69. In combination with a nail machine, the feed consisting of the lower plate,
and the upper oscillating feed dog co-operating with said plate and carrying the
vertically adjustable gripping bar, for the purpose explained.
70. In a feed for nail machines, the trunnioned feed dog, having a vertical socket,
a gripping bar mounted in said socket, and a set screw for adjusting said gripping
bar, substantially as and for the purpose explained.
71. In a nail machine, the combination of the feed devices, and the adjacent
nippers consisting of the fixed and movable jaws, the eccentric shaft and the
connecting link between the movable jaw and said eccentric shaft, substantially as
and for the purpose explained.
72. In a nail machine, the combination with the upper and lower tension or
straightening rolls and the eccentric shaft for separating them, of the fixed and
movable nipping jaws and the connecting link between the movable jaw and the
eccentric shaft, substantially as and for the purpose explained.
73. In a nail machine, the combination of the feed and the easing and guiding
roller, supported in a frame having flaring jaws for guiding the wire into the roller,
substantially as and for the purpose set forth.
74. In a nail machine, die blocks each having thereon a gripping die and also a
pointing and cutting die, substantially as and for the purpose set forth.
75. In a nail machine, die blocks provided with cutting dies movable thereon,
and rocking bearings between the die and block, as explained.
76. In a nail machine, the combination of a die block having a cavity, a cutting
die loosely mounted in said cavity and a convex bearing seat for said die, as.
explained.
77. In a nail machine, die blocks having cutting and pointing dies movably
mounted thereon, the adjusting wedges for said dies and the convex blocks
interposed between the wedges and dies, as explained.
78. In a nail machine, the combination of the die blocks, gripping dies on said
blocks for holding the nail while it receives its head, cutting dies mounted in
recesses in the blocks and cap-plates having lugs also fitting in said recesses to hold
the dies in place and receive impact of the hammer and sustain and strengthen the
die block, as explained.
79. In a nail machine, the combination of the oppositely reciprocating gripping
and cutting dies, and an expeller consisting of a projecting arm having a notched
end located in the line of the feed and holding the nail and preventing it from

page_text: sticking in either of the dies as they recede from the centre and allowing the nail
to drop out of the way, as explained.
80. A nail machine, and the various parts thereof, when constructed substantially
as described in the foregoing Specification and shown in the drawings hereunto
annexed.
1001
ROBERT POWELL,
By Harris & Mills,
23, Southampton Buildings, London, W.C., Agents.