Improvements in Horse Shoe Nail Machines.
Year: 1893

page_text: Date of Application, 16th May, 1693-Accepted. 24th June, 1893
COMPLETE SPECIFICATION.
Improvements in Horse Shoe Nail Machines.
I, WILLIAM HENRY DAYTON, Machinist, of Torrington, State of Connecticut,
United States of America, 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 :-
This invention relates to an improvement in horse-shoe nail machines, the object
being to provide a machine for automatically feeding horse shoe nail blanks to
reducing or swaging dies whereby the shank of the nail is reduced to a tapering
With this object in view the invention consists in
certain novel features of construction and combinations of parts as will be
hereinafter described and pointed out in the claims.
form circular in cross section.
In the accompanying drawings,
Figure is a plan view of the improved machine.
Figures 2 and 3 are views in side elevation of the opposite sides of the machine.
Figure 4 is a view in end elevation, certain of the parts being shown in vertical
section.
Figure 5 is a longitudinal section.
Figure 6 is a transverse section taken through the head and reducing or
Swaging dies.
Figure 7 is a detached view in end elevation of the head of the machine and a
portion of the blank-feeding machine.
Figure 8 is a view in side elevation of the gripping jaws.
Figure 9 is a plan view of the same.
Figure 10 is a detached view showing the blank carrier and raceway.
Figure 11 is a detached view showing the lower end of the shaft which passes
through the hopper and the cam for reciprocating the shaft.
Figure 12 is an edge view of one of the headed blanks.
Figure 14 represents the blank after swaging.
Figures 15 and 16 represent side and edge views of a finished horse-shoe nail.
A represents a hollow standard, the lower end of which is provided with flanges c
to which are secured the feet which serve to insure a sufficiently extended
bearing for the machine to retain it steady while in operation. The upper end of
standard A is furnished with a cylindrical bearing in which is supported the sleeve a
having the cylindrical head B formed integral therewith. The sleeve and head are
Within the sleeve
secured against movement or displacement by the set screw a¹.
or elongated bearing a is journalled the shaft D to the outer end of which is
fastened a pulley D' through which power is transmitted to the shaft. The
opposite end of the shaft D has either formed integral therewith or secured thereto
the rotary head D2 which is provided with a transverse slot within which are
placed the dies FF, and the sliding hammer blocks G G. Between the cylindrical
inner wall of the stationary head B, and the outer periphery of the rotary head D2
are placed the rings H H. Each one of these rings is provided with any desired
number of radial slots d which extend from the outer periphery of the ring partly
through its width. Within these slots d are placed the pintles e which are
constructed with square or angular ends and cylindrical central portions. The
angular shaped ends of the pintles fit within the slots in the rings H H and hence
are prevented from rotating, while they are allowed a radial movement. Upon the
pintles are journalled the rollers I and hence as will be observed a series of rollers
is interposed between the stationary and the rotary head. The rings H H are
fastened together by pins, so that the rollers are kept in alignment. To the outer
face of the rotary head is secured by suitable screws the centering plate J, which

page_text: is constructed with a concave recess having a central aperture 11 through which
latter the blank is fed to the dies. On opposite sides of plate J, are located the
adjusting plates K, each of which is furnished with elongated slots k, k, through
which the bolts ¹ extend into the rotary head. By means of the nuts ² the
plates K are secured in any desired adjustment. Each hammer block G G is
provided with an elongated recess into which extends a pin fastened to the
plate K. By varying the adjustment of the plate the throw or range of movement
of the hammer block may be readily regulated. On the inner face of each die F-
is formed a groove tapering throughout its length and semi-circular in shape, so
that when placed together the two grooves are of the form to which the shank and
the underside of the head, or the shoulder connecting the head and shank of a nail
blank, will be reduced by the swaging operation. The series of rollers and the
rings in which they are mounted are retained in place by means of the annular
face plate K² which is fastened in the stationary head B. The shaft D being
rotated rapidly operates to impart a rapid motion to the rotary head the effect of
which is to throw the dies F F and hammer blocks G G outwardly by centrifugal
force, but as the rear ends of the hammer-blocks come in contact with the rollers I,
the latter operate as rolling abutment and serve to force the hammer blocks and
dies radially inward and thereby impart a swaging blow upon the blank between
the dies. The rollers I are arranged in pairs the two rollers of each pair being
located on diametrically opposite sides of the centre of the rotary disk so that the
two dies FF are forced inwardly and caused to act simultaneously on the opposite
sides of the blank. By arranging a series of rollers I within the head, a number
of blows will be given the blank at each revolution of the head. In the drawings
I have shown six pairs of rollers, and hence the blank is subjected to six blows on
the opposite sides at each revolution of the rotary head.
To the stationary head B are bolted the brackets L L with which are connected
or cast integral the bed piece or frame L' which extends horizontally outward in
front of the head. M is a reciprocating table the side edges of which are supported
in suitable guides M', M. Upon the rear end of table M are mounted the
posts m, m, in which is journalled the rocking bar m'. The screw threaded end m²
of a connecting rod M2 is inserted through a hole formed in the rocking bar m
and is adjustably secured thereto by means of the nuts m³ and m². The outer
end of connecting rod M2 is pivotally connected to the upper end of the lever N
which is journalled on the shaft N'. The shaft N₁ is supported in bearings
formed in the depending brackets N2 N2 fastened to the bed or frame L. To
the lower end of arm N³ or lever N is secured one end of a spiral spring (
the opposite end of which is fastened to the standard A. Spring exerts its
power through the lever N to pull the table M to the limit of its rearward move-
ment. The forward movement of table M is effected through the action of the
cam P on the friction roller P₁ journalled in the end of an arm P² formed or
rigidly connected with lever N. The cam face formed on the periphery of cam 1'
acting upon the friction roller P, serves to force the latter downward, and as the
lever N and arm P2 together form a bell-crank lever jourualled at N¹ the bell
rank lever is rocked on its bearing by the depression of the arm P2 and the
table M is moved forwardly toward the head of the machine. Cam P is fastened
to a driven shaft Q journalled in depending bracket bearings Q', Q¹. To one end
of shaft is secured a worm gear Q with which meshes a worm Q³ on the
longitudinally arranged driving shaft R which is journalled in bracket bearings
attached to the side of the machine. R is a clutch on shaft R and R2 is a clutch
lever for moving the sliding member of the clutch into and out of engagement
with the fixed member. Shaft R is provided with a band pulley S, through which
power is transmitted to revolve the shaft and mechanism connected therewith.
Upon the reciprocating table M is mounted the bearing plate M² which is
secured between laterally adjustable bearings 2 2 which engage its side edges.
Plate M2 is provided with end bearings or guides in which reciprocate the
gripper head or stock T. Figs. 8 and 9 are detached views of the gripper head

page_text: and jaws. 1 is a central yoke provided at its forward end with a tubular arm 2 to
the outer end of which is connected or is formed integral therewith the bifurcated
gripper head 3. Within the transverse slot 4 in the head are pivoted at 5, 5, the
gripping jaws 6, 6, the outer end of which are curved and are provided on their
meeting faces with recesses 7, 7, so formed that when the jaws are closed they will
firmly grasp the head of a horse shoe nail blank. The opposite ends of a spring
bail 8 engage in recesses 9, 9, formed in the rear ends of the jaws and serve to
retain them normally open, by forcing their rear ends towards each other. A
toggle lever consisting of the lever arms 10, 10 and 11, operate to reciprocate the
wedge pointed rod by which the gripper jaws are closed and opened at the proper
times to grasp and release the nail blank. The lower end of one of the arms 10
is pivoted to the rear end of the sliding bar 12 which is supported so as to slide
freely within the tubular arm or sleeve 2. The forward end of bar 12 is provided
with a wedge 13 which engages the rear ends of the gripping jaws 6, 6, and serves
to force their rear ends apart and thus close their forward and gripping ends.
When the wedge is retracted the spring bail operates to force the rear ends of the
jaws toward each other and thereby separate their outer ends. The lower end of
the outer toggle arm 10 is pivoted to the screw plug 14, which is adjustably
secured within the tubular arm or stock 15 connected with the rear end of the
yoke 1. Within the rear end of the stock 15 is screwed a bolt 16, the end of
which is provided with an angular shaped head 17 to admit of the adjustment of
the bolt. Head 17 abuts against a stout flat spring plate 18 which is provided
with open slots 19, 19, at its opposite ends. Within these slots extend the
pins 20, 20, on the posts 21, 21, attached to the reciprocating plate or bed piece M.
By means of the spring plate 18, the gripper stock and gripping jaws are allowed
a slight yielding movement which insures an easy action to the different parts of
the mechanism connected with the gripping jaws and further the spring plate takes
up any slight lost motion which results from the uneven wear of the parts. The
upper ends of the arms 10, 10, are pivoted to the lower end of arm 11, the upper
end of which is pivoted to the rocking arm 22. Arm 22 is constructed with a
sleeve 23 which is mounted upon a rock-shaft 24 and is adjustably secured thereto
by a set screw 25. When the outer end of the rocking arm 22 is raised as
illustrated in Figure 5, the wedge is withdrawn from the rear ends of the gripping
jaws thereby allowing the spring bail to open their forward or gripping ends.
When the rocking arm is moved in the opposite direction, the toggle levers are
moved into the position shown in Figures 8 and 9, which results in the wedge being
forced between the rear ends of the gripping jaws and firmly closing their forward
and gripping ends.
To one end of the rock shaft 24 is rigidly secured the crank-arm 26 provided at
its outer end with a crank pin 27 which latter engages a groove 28 formed in the
vertically reciprocating frame or plate 29. The plate 29 is fitted to move vertically
within guides 30 30 attached to the side of the machine frame. A roller 31 is
journalled in the lower end 32 of plate 29 and engages a cam 33 which is fastened
on the revolving shaft Q. Cam 33 represented in dotted lines in Fig. 3 is there
shown when moved to a position to partly close the toggles. It revolves in the
direction indicated by the arrow, and by the engagement of the roller 31 with that
portion of the cam face between 34 and 35, the roller and plate are gradually raised
until the toggle arms have been depressed and the wedge firmly driven between the
rear ends of the gripping jaws. It will be observed that the cam is furnished with
a slight projection at 35 the purpose of which is to drive the wedge forcibly between
the jaws at the outset, and then the cam drops back slightly and rests upon the
cam surface 36 whereby the cam roller and crank pin are relieved of any undue
strain or wear during the revolution of the cam, the strain or thrust being borne
by the toggle arms the pivotal bearings of which are then in alignment and spring
plate which latter receive the end thrust on the toggle arms.
When the cam has
made nearly a complete revolution, the straight face 37 will travel past the roller,
and allow the latter to fall suddenly within the slot formed in the cam. This will

page_text: allow the plate or frame 29 and crank arm 26 to fall by their gravity and thereby
raise the toggle arm 11 and withdraw the wedge from between the gripping jaws
and allow the spring bail to open their gripping ends and release the blank held by
them. In order that the parts may act promptly in releasing the blank, I provide
the cam 33 with an arc shaped face cam 38, which is flush on its outer periphery
with the periphery of cam 33. When cam 33 has revolved so that the cam 38
comes beneath the lower end 39 of the plate of frame 29, the latter will be supported
by cam 38 and will ride thereon until the roller has been carried over the slot.
When the end of cam 38 has travelled so as to release the plate, the latter will
quickly drop into the slot with the result already explained. The rear end of the
gripper head is provided with an annular flange 40 between which and the bearing th
are placed on the tubular arm 13 suitable leather or other elastic washers (not
shown) which serve to deaden the noise and shock of the parts when the gripper is
suddenly forced forward on the release of the blank.
41 represents a conically shaped hopper into which the nail blanks are placed
and from which they are automatically fed to the swaging dies. Hopper 41 is
fixed to a vertically arranged sleeve 42 the lower end of which is provided with a
bevel gear 43 which meshes with a bevel gear on the transverse shaft 44. To the
opposite end of shaft 44 is secured a worm gear 45, which meshes with a worm 46
on the shaft R. Any suitable clutch (not shown) may be employed for throwing
the worm 46 into and out of engagement with the shaft R. By the gearing above
described a rotary motion is imparted to the hopper and its contents. To a
bracket 47 fastened to the stationary head B, is secured a curved race-way 48,
which consists of the side pieces 49, 49, separated sufficiently to receive the shank
portions of the blanks, but on the other hand they are sufficiently close so that their
outer edges 50, 50, will form bearings for the heads of the blanks as represented
in Figs. 2, 4 and 7. A curved guard 51 is secured above the race way and serves
to prevent the end wise diplacement of the nail blanks. A pick-up arm 53 is pivoted
at 55 to a bracket connected with the race-way or any other suitable support
adjacent thereto. This arm consists of the two bars or plates 54, 51, see Fig. 1,
which are separated so as to form a slot 55 extending the entire length of the arm.
This slot is of such width that it will readily receive the shank portion of a nail
blank, but too narrow to allow of the passage through it of the head of the blank.
Located above the bars 54, 54, is a guard plate 56, the space between the guard
plate and the guide bars being slightly greater than the depth of the head of the
blank. One end of the guard plate 56 is bifurcated, the slot 57 being of less width
than that of the head of the blank. 58 represents a vertical movable rod which
extends downwardly through the hopper and the sleeve 42. The lower end of the
rod is suitably pointed and rests upon a cam 59 fastened to the shaft 44, a detached
view of the cam and lower end of the rod being given in Fig. 11. Hence it will
be observed that at each revolution of shaft 44, the rod 58 has a vertical movement
imparted thereto. To the rod 58 is adjustably secured by the set screw 60, a
horizontal arm 61, the outer end of which is provided with an elongated slot 62
through which passes a pin 63 fastened to the pick-up arm 52. Thus by the
vertical movement imparted to rod 58, the pick-up arm 52 is oscillated on its pivotal
bearing.
The hopper being filled with nail blanks is rotated and during a portion of
every complete revolution the pick-up arm will project downwardly into the blanks
contained in the hopper as illustrated in Figures 1 and 2 and ordinarily a few
blanks will be caught between the fingers of the pick-up arm in such a manner that
the heads of the blanks will rest upon the surfaces of the bars 54, 54, while the
shank portions will depend through the slot formed between these arms. When
the cam on shaft 44 raises the rod 58, the arm 61 is raised and the pick-up arm is
tilted so that the beveled face 64 on the under side of the short arms of the
bars 54, 54, will rest upon the inclined faces 65, on the race-way. It will be
observed that the slot 57 in the end of guard plate 56, and the slot 55 formed
between the ends of the bars 54, 54, while of less width than that of the heads of

page_text: the blanks, is sufficiently wide to allow the end 64 of the curved and stationary
guard 51 to pass through them. When the pick-up arm is tilted into the position
described, its angle will be sufficiently sharp to cause the nail blanks to slide by
their gravity into the curved raceway. While the pick-up arm will not act to
pick-up any predetermined number of blanks at each revolution of the hopper still
experience has demonstrated the fact that it will keep the race-way always supplied
with blanks. The following provision is made for preventing the pick-up arm
from picking up blanks when the race-way is completely filled. Suppose the
race-way is filled to the point 69. The pick-up arm on being tilted will allow
the blanks contained therein to slide down into contact with the uppermost blank
in the race-way, but owing to the fact that the heads of the blanks remaining in
the arms of the pick-up will engage the stationary guard 51 and thereby lock the
pick-up arm in its tilted and feeding position, the vertically movable rod 58 will be
upheld during the next succeeding revolution of the hopper and the pick-up arm
will thus be maintained out of contact with the blanks in the hopper. As the cam
engages the rod 58 on the next revolution, it will slightly raise the long arm of the
pick-up and so lessen the frictional contact of the blank heads with the guard 51,
that the blanks remaining in the pick-up arm will slide into the raceway and
provided the latter has been emptied of a sufficient number to receive all of those
remaining in the pick-up arm, the latter will be released and tilt back again into
the hopper, when it will again operate to collect another supply of blanks. Thus
it will be observed that the pick-up arm not only automatically collects a charge of
nail blanks and feeds them to the race-way, but it is also automatically prevented
from collecting a further supply of blanks so long as the race-way is fully
charged.
I will now describe the mechanism for carrying the blank from the race-way and
delivering it to the gripping jaws. 70 is a sector shaped carrier, the hub 71 of
of which is fastened to the rock shaft 72 by means of a set screw 73. Rock-shaft 72
is journalled in a tubular bearing 73", and is provided with a bevel gear 74 with
which meshes a sector gear 75 attached to the arm 76 of a bell crank lever which
is pivoted at 77. The other arm 78 of this lever has an anti-friction roller 79
journalled in its end, which engages a cam 80 fastened to the shaft Q. A spiral
spring 81 is fastened at one end to the arm 78 while its opposite end is fastened to
the frame of the machine. Spiral spring 81 serves to move the sector gear 75
upwardly and thus rotate the shaft 72 in one direction while the cam 80 operates
through the arm 78 to move the sector gear downwardly and thus rotate the
shaft 72 in the opposite direction. Sector carrier 70 is constructed with a
peripheral bearing 81 which as will be observed by reference to Figs. 2 and 10
moves in close contact with the lower end of the race-way and serves as a support
for the blanks therein contained. The movement of the sector carrier is regulated
and adjusted by means of the set screw 82. The forward end of the peripheral
bearing 81 is cut away thereby forming a shoulder 82. A jaw 83 is secured to a
pin 84 pivoted in the forward end of the carrier. One end of a pivoted lever 85
impinges against a beveled face 86 formed on the tail piece of jaw 83, while a
spiral spring 87 secured at one end to the lower arm of lever 85 and at its opposite
end to the sector carrier serves to move the jaw 83 toward the shoulder 88 on the
carrier. A stud 89 is secured to the pin 84. When the carrier is moved to the
position shown in Fig. 10, the stud 89 will engage the side of the race-way and
slightly rotate the pin 84, and the jaw 83 thereto attached and thus form an
opening of sufficient width between the opposing faces of the jaw 83 and
shoulder 88 for the admission of a nail blank which will drop therein. When the
carrier is moved forwardly, the stud 89 is moved out of contact with the race-way,
and hence the spring 87 will operate through the lever 85 to cause the jaw 83 to
firmly grasp the shank of the blank and retain it against displacement. The blank
as thus grasped by the jaws of the carrier is represented in Fig. 12, the head of
the blank projecting outwardly from the side of the carrier. The carrier is then
automatically moved from the position shown in Fig. 10 to the position shown in

page_text: Fig. 7 and just before it has reached the latter position, the gripping jaws are
automatically retracted so as not to obstruct the passage of the projecting heads of
the nail blank. When the carrier is in the position shown in Fig. 7, the nail
blank is brought into alignment with the opening between the dies FF while the
head of the blank is brought into alignment with the recess formed in the gripping
jaws. The machine then automatically advances the gripping jaws which are
open and receives the head of the blank and then the jaws are firmly closed around
the head. The carrier is then retracted and as the jaws serve to retain the head
firmly grasped between them, the spring jaw on the carrier releases its hold on the
shank of the blank.
Within a socket 90 on bracket 47 is removably secured a funnel 91 for the
reception of oil which is gradually fed by means of a wire guide to the blank as it
is being swaged.
Having described the function and relative arrangement of the various parts of
my improved machine I will now give a brief description of its operation, and will
first explain the method of forming the blanks which are supplied thereto. I first
take any suitable wire-preferably of Siemens and Martins steel and cut it into
suitable lengths to form blanks. These blanks are then headed in any suitable
heading machine thereby producing headed blanks of the form illustrated in
Fig. 13.
The hopper 41 is filled or partly filled with headed blanks of the form illustrated
in Fig. 13. During nearly a complete revolution of the hopper and its contents,
the pick-up arm projects downwardly into the blanks with the result that ordinarily
one or a number of blanks will be caught between the arms of the pick-up. At
every revolution of the hopper, the pick-up arm is tilted and its charge of blanks
is delivered to the curved race-way within which the blanks are retained by the
periphery of the sector carrier, and when the carrier is moved into the position
illustrated in Fig. 10, its jaw will be opened and a blank will fall between the jaw
and stationary shoulder on the periphery of the carrier. As the carrier is moved
the spring actuated jaw serves to hold the blank firmly in place while the periphery
of the carrier retains the remaining blanks within the race-way from dropping out.
The blank is carried by the carrier into the position shown in Figs. 1, 3, 5 and 7,
whereby it is brought into alignment with the tapering groove formed on the
meeting faces of the dies F, F. On the passage of the blank from the race-way to
the dies, the gripping jaws are slightly retracted to make room for the passage of
the projecting head of the blank. When the blank is in the position referred to,
table M is moved forward by the action of cam P, thus moving forward the
gripping jaws which are in their open position. When the jaws have been moved
forward a sufficient distance to cause the head of the nail to enter the recesses 77
formed therein, the arm 26 will be raised through the action of cam 33 and depress
the toggle arms and force the wedge 13 forwardly and between the rear ends of the
gripping jaws thereby closing their forward ends and firmly clamping the head of
the blank between them. Owing to the fact that the three pivotal bearings of the
toggle arms 10 10 are brought into alignment when fully depressed, the wedge 13
is securely locked against retraction until the blank is ready to be discharged.
After the head of the blank has been thus grasped by the gripping jaws, the sector
carrier is moved backwardly its spring jaw yielding to permit of its disengagement
from the shauk of the blank. Table M continues to advance and feeds the shank
of the blank into the tapering groove formed between the dies F F. The outer
ends of these semi-circular grooves are as will be observed made flaring so that in
connection with the concave face plate J, the end of the shank is guided into the
groove between the dies. Hence it will be seen that the head of the blank is firmly
held between the gripping jaw, while the shank of the blank is gradually fed
forward as it is being swaged by the action of the dies F F. Owing to the fact
that the dies are caused to act with great rapidity, imparting a number of blows to
the blank during each revolution of the head D, the reduction of the blank is
effected quite rapidly and it is quickly swaged into the form illustrated in Fig. 14,

page_text: The swaging operation imparts a smooth and highly finished surface to every
portion of the shank and underside of the head, and renders the shank perfectly
tapered and circular in cross section throughout its length. The blank is subjected
to the action of the swaging dies throughout the time the roller P¹ engages that
portion of the periphery of cam P from the point 92 to 93, and then the gripper
jaws are retracted and reach the limit of their outward movement when roller P¹
engages the point 94 in cam P. After the gripping jaws have been retracted, the
end of face cam 38 will pass from beneath the lower end 32 of the plate 29 and
allow the latter to drop and thus through the medium of the crank arm 26, and
toggle lever withdraw the wedge 13 from between the rear ends of the gripping
jaws and permit bail to open the jaws and release the swaged blank, which drops
into a suitable receptacle 95 bolted to the supporting frame of the machine. When
in the revolution of cam P the roller P has reached the point 94, the grippers will
have been retracted to their extreme limit of movement, and while in this position
the carrier moves past the outer ends of the gripping jaws the latter being
sufficiently retracted to offer no obstruction to the projecting head of the blank.
During that portion of the revolution of cam P in which roller P¹ engages the cam
surface between the points 94 and 96, the gripping jaws will be moved forward a
distance sufficient to cause the head of the blank to enter the recesses 77 in the
forward ends of the jaws and as soon as this point is reached the jaws are auto-
matically closed, and the plate is moved forward by the action of the rollers P¹ on
that portion of cam F between the points 96 and 92 whereby the shank is fed into
the tapering opening between the dies F F. Cam 80 on shaft Q is so arranged
with relation to cam P, that while the blank is being swaged, the sector carrier
will be moved rearwardly and receive another blank and by the time it has been
moved forwardly again and into a position to feed the blank to the gripping jaws,
the latter will have withdrawn and discharged its swaged blank and will be in
position to receive a fresh blank.
The blanks after having been swaged, are annealed and are then flattened
between suitable dies which results in the production of a completed nail as
illustrated in Figs. 15 and 16.
It is evident that many changes might be made in the form and construction and
relative arrangement of the various parts of my improved machine without
involving a departure from the spirit and essence of the invention and hence would
have it understood that I do not limit myself to the particular construction and
arrangement of parts shown and described, but,
Having now particularly described and ascertained the nature of my said inven-
tion, and in what manner the same is to be performed, I declare that what I
claim is :-
:―
1. The combination with a rotary head and swaging dies carried thereby, of a
reciprocating table, a gripping jaw head or stock carried by the table, and a spring
for receiving the end thrust of the head or stock, substantially as set forth.
2. The combination with a rotary head swaging dies and sliding hammers, of a
face plate constructed with a conical recess and a central aperture; adjustable
plates secured to the face of the rotary head, and pins fastened to the adjustable
plates, said pins entering elongated recesses in the sliding hammers and regulating
their throw, substantially as set forth.
3. The combination with a reciprocating table, a rock-shaft and yielding stock
mounted on said table, pivotal gripping jaws connected with one end of the
yielding stock, a sliding rod 12 provided with a wedge for closing the jaws, toggle
levers 10, 10, 11 and means for actuating the rock-shaft and thereby insuring the
opening and closing of the jaws, substantially as set forth.
4. The combination with gripping jaws and a reciprocating rod having a wedge
pointed end, of toggle levers, rock-shaft, crank arm, vertically movable plate
provided with a guide way for the reception of a pin on the crank arm and a cam,
substantially as set forth.

page_text: 5. The combination with gripping jaws mounted in a yielding stock, of a wedge
for closing the gripping jaws, toggle levers, a cam provided with a projection as
at 35 to force the pivotal bearings into alignment and subject the stock to the
tension of its spring abutment, and means for transmitting motion from the cam to
the toggle substantially as set forth.
6. The combination with the gripping jaws, reciprocating wedge toggle-levers
and oscillating arm, of a vertically movable plate, and a cam provided with a recess
and with a face cam 38 which latter supports the vertically movable plate until it
can drop suddenly into the recess in the cam and thereby cause the sudden opening
of the gripping jaws, substantially as set forth.
7. The combination with the reciprocating plate M and laterally adjustable
plate mounted thereon, of the gripper stock or head mounted in said laterally
adjustable plate, substantially as set forth.
8. The combination with a rotary head and swaging dies carried thereby, of a
reciprocating table, gripping jaws mounted in a stock yieldingly and laterally
adjustably mounted on said reciprocating table, and means for opening and closing
said gripping jaws, substantially as set forth.
9. In a horse-shoe nail machine, the combination with a rotary head and swaging
dies carried thereby, of a race-way for receiving headed blanks, a rotary hopper, a
pick-up arm, means for actuating the pick-up and causing it to convey blanks from
the hopper to the race-way, and means for automatically preventing the pick-up
arm from gathering blanks until it has first discharged all of the blanks held
thereby into the race-way, substantially as set forth.
10. In a horse shoe nail machine the combination with a race-way and gripping
jaws, of an oscillating blank carrier, a bevel gear 74, sector gear 75, bell-crank
lever 76, 78 and cam 80, substantially as set forth.
11. In a horse shoe nail machine the combination with a rotary head and swaging
dies carried thereby, of a reciprocating table, a stock mounted on said table,
means to provide a yielding lengthwise movement to said stock, gripping jaws
connected with the stock, means for reciprocating the table and thereby moving
the jaws to feed and retract the blank, substantially as set forth.
12. In a horse shoe nail machine, the combination with a rotary head and
swaging dies carried thereby, of a reciprocating table, a stock mounted on said
table, means for imparting a lateral adjustment to the stock, means for providing a
longitudinal yielding movement to the stock, and gripping jaws and means for
actuating the same combined with said stock, substantially as set forth.
13. In a horse shoe nail machine the combination with a reciprocating table, of
the gripping jaw stock, uprights 21, 21 and spring 18 provided at its ends with open
slots 19, 19, substantially as set forth.
14. In a horse shoe nail machine the combination with a rotary head and swaging.
dies carried thereby, of a reciprocating table, a gripping jaw stock mounted on said
table, means for adjusting the stock laterally, means for allowing the stock an
endwise yielding movement, and toggle levers for reciprocating a wedge for closing
the jaws, substantially as set forth.
15. In a horse-shoe nail machine the combination with a standard provided with
a cylindrical bearing at its upper end, sleeve a mounted in said bearing and
adjustably secured therein by the set screw a', stationary head B formed on one
end of sleeve a, a shaft D journalled in said sleeve; rotary head formed integral
with one end of the shaft, and a band pulley secured to its opposite end, substantially
as set forth.
R. HADDAN,
Herbert Haddan & Co.,
18, Buckingham Street, Strand, London, Agent for Applicant.