Year: 1886

page_text: «
I, FERDINAND PHILIPS, a subject of the Empire of Germany, but domiciled in
the United States of America, at the City of Philadelphia, in the County of
Philadelphia, and State of Pennsylvania, Civil 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 that class of Bolt Heading Machines in which the blank
to be headed is held firmly by one end in a die or holder beyond which the end of
the blank upon which the head is to be formed projects, in such manner as to admit
of its being operated upon when heated to the proper temperature by a series of
five hammers, which successively work it end wise and laterally to a square or
hexagon or other shape, as is well understood. The hammer which acts upon the
blank endwise, or in the direction of its axis, and which upsets the projecting end
of the blank, is called the header, while the other four hammers which all act upon
the blank laterally move in pairs towards the axis of the blank as a common
centre, all four in a common plane vertical to that axis, and one pair at right
angles to the other; one of these pairs having their movements in a horizontal
direction, are designated as the side hammers, while the other pair, having the same
movements, but in a vertical direction, are designated as the top and bottom
hammers.
These four lateral hammers are made of steel, and each is mounted on a slide,
which in turn is fitted to move in a guide formed in a cast iron frame called the
spider." These slides and guides are all more or less subject to wear, but the
bottom hammer slide is especially worn rapidly by reason of the cinders (iron
oxide) accumulating thereupon, and from the water used to keep the dies and
hammers cool, falling, as it does, directly upon this hammer guide, and thus causing
it to completely wear out in a comparatively short time.
The main object of my invention is to entirely avoid the wear, and I accomplish.
this object by dispensing entirely with any necessity for the slides and guides here-
tofore used. Another new feature of my improved bolt header consists in the
combination of certain devices for moving the header, and providing means for
taking up any lost motion resulting from wear of the parts by which this header
is worked. Another new feature of my improved bolt header consists in the
manner in which the four lateral hammers are moved. These are the novelties

page_text: -
relating particularly to the hammers and their mode of operation, whilst my inven-
tion still further embraces features relating to the blank dies and blank carriage, as
will be hereinafter fully described.
In the accompanying drawings, the position of the parts shown is that occupied
by them when the header is at the forward end of its stroke.
Figure 1 is a vertical longitudinal section through the machine. Fig. 2 is a
portion of the spider, with the lower hammer suspended in position. Fig. 3 is a
front view of my improved lateral hammer system, mounted upon the frame of the
machine as shown in section. Fig. 4 is a section on the line x, x, of Fig. 3. Fig. 5
is a detailed view of my improved bottom hammer guide with a portion of the
frame. Fig. 6 is a diagram, illustrating the operation of the lower hammer when
it has a parallel guide motion. Fig. 7 is diagram, illustrating the operation of the
lower hammer when it has a straight-line-guide motion, as will be hereinafter more
particularly described.. Fig. 8 is a plan view of my improved bolt header, certain
parts of which being shown in section and certain parts relative to the movement
of the die carriage being left off, and Figs. 9 to 16 relate to the holding dies and
blank carriage, and will be hereinafter more fully enumerated and explained.
A is the main frame of the machine mounted upon the legs B, B, and bed plate C.
This frame A, is provided with bearings a, a, (Fig. 8) to receive the crank shaft D,
which gives motion to the header H, and which header is guided in the main frame,
in the manner shown and as is well understood. The crank shaft D, and header H,
are connected by a link L, terminating in a cylindrical knuckle joint k, parallel to
the crank shaft D, which abuts against a brass box b, recessed into the header, as
shown in Fig. 1, and firmly held in position by two rods r, r, and a back guide E,
which is guided in the main frame A, in a similar manner as is the header H.
The guide E, and link L, are kept in close sliding contact on their abutting
services e, e; the cylindrical curve of these sliding surfaces being struck from the
axis of the knuckle joint k, as clearly shown in Fig. 1. Any wear that may be
produced in the knuckle joint k, and its brass box b, or on the abutting surfaces e, e,
of the link L, and back slide E, may be readily taken up by tightening the rods r, r,
by means of the nuts n, n, n, n. Thus the crank shaft D, connecting link L, knuckle
joint k, brass box b, header H, and back slide E, may be kept relatively in good
working condition for practically an unlimited length of time.
With the header H, are connected four levers, of which two, F and F¹, are seen
in Fig. 1. The inner end of the lever F,'is connected with the header H, by means
of a pin p, through a jaw j, formed in the header. In order that the fulcrum of the
lever F, may be moved slightly up and down, when the header H, moves hori-
zontally to and fro, I connect the fulcrum f, with a rigid portion of the machine by
a compensating link l, as shown in Fig. 1. The lever F¹, has a rigid fulcrum f¹.
In order to admit of the up and down motion produced by the vibrating motion of
the lever F¹, around the fulcrum f', I do not connect the one end of the lever F¹,
in a rigid manner with the header H, but I admit of the vertical motion by
permitting the lever to work in a slot or recess cast in the header, as shown in
Fig. 1. The header H, and lever F¹, may be connected by a pin, and the fulcrum f¹,
arranged in the same manner as on the top hammer, but I prefer the manner
described, as I am enabled thereby to readily remove the lever F¹, without
removing the header from its seat, which would (in case of emergency) be
necessary if otherwise constructed in order to withdraw the pin similar to the
pin hereinbefore referred to. The other ends of the levers F and F¹, are connected
by means of rods R and R¹, with toggle joints T and T¹. Whilst the header is
moving towards the bolt blank 6', held in the dies d'and d, the toggle links are
moving into the position shown in Fig. 1, drawing the hammer guides G and G¹,
respectively, upward and downward, and with them the hammers h and h¹. It will
thus be seen that they are now sufficiently out of the way of the header, or, as it
is technically termed, they "clear." On the return stroke of the header the
toggles T and T, will straighten out gradually, the relative disposition of the
levers F and F¹, to the movement of the header being such that when the header

page_text: is withdrawn to the full extent of its stroke the toggles T and T¹, are brought into
a straight line and produce the blows of the top and bottom hammers on the bolt
head. To facilitate the adjustment of the toggles relative to the header, as above
described, the rods R and R² are provided with male and female screws, by means
of which said rods can be lengthened or shortened to fulfil the above conditions.
Such an arrangement I have shown in Figs. 1 and 8 of the drawings.
The side haminers h³ and h³, (Fig. 3) are moved by the header in a similar
manner as the top and bottom hammers, but in order that the side hammers
may clear the top and bottom hammers, the connections are arranged relatively in
such manner that the toggle joints T and Ts, of these side hammers are in a
straight position when the header is in the middle of its stroke, whilst, as afore-
said, the top and bottom toggle joints are straight that is, when the header is in
its farthest position from the face of the dies d and d¹. This effect upon the
"timing" of the blows struck by the side hammers relatively to the blows of the
header, is produced by simply lengthening the rods R2 and R3, of the side hammers,
80 as to move their toggles T and T, past their straight position in both
directions, but in order to obtain the proper amount of motion for each blow thus
imparted to the side hammers, I also arrange the proportions of the levers
actuating these toggles by changing the position of their fulcrums f³ and ƒ³,
accordingly, as shown in Fig. 8.
The rods R and R³, as shown in Fig. 8, are adjusted in such a manner that the
toggle link is in a straight position 4, 5, 6, when the header with the inner end of
the levers 1 and 2, is in the centre 3, of its motion backward, and whilst the
header is passing its central position, the toggle link is moving towards its final
position 4, 7, 8, and when it reaches this position, the header is all the way back.
The side hammers h and h³, are out of the way of the top and bottom hammers,
and the top and bottom hammers are all the way in, as heretofore described. It is
evident that the side hammers will then strike the bolt head each time when the
header passes its central position, that is to say, coming and going, whilst the top and
bottom hammers strike the bolt head but once in each revolution of the crank shaft.
This described difference in the number of blows struck has on the one hand no
injurious effect on the bolt head, while the simplicity and easy motion of this
improved toggle mechanism, actuated solely from the reciprocating header, prevents
rapid and injurious wear of its parts, which are of plain construction and always
readily accessible for adjustment or repairs.
The most important feature, however, of my improved bolt header consists in the
device for guiding the bottom hammer. In all the machines as heretofore con-
structed similar to the one represented in sheets 1 and 4, of the accompanying
drawings, the hammers were fastened to guides G, sliding in grooves of a casting S,
Figs. 1, 2 and 3. To prevent the rapid wear of the hammer slide G, these grooves
have been lined with gibs g, of hardened cast steel, but the destroying effect of the
cinders falling as they do together with the water used in bolt forging, as is well
understood, on the lower slide, wear it out so rapidly and completely that the lower
hammer soon yields in every direction, and thus prevents the formation of a perfect
bolt head. Aside from this, however, absolutely no dependence could be placed
upon the lower hammer as heretofore arranged. It was a source of constant repair
in all machines working with four lateral hammers.
To overcome these serious difficulties is one of the objects of my invention, which
I accomplish by dispensing with the sliding guides for the bottom hammer
altogether, and guide the same by links, as hereinafter more fully described.
Figure 6 showing the principle of such a guide.
O and O¹ are stationary points, m and n are the links, and t is the hammer. It
is obvious that when the links swing around the points o and o¹, the hammer will
be guided parallel to its previous position and parallel with the blank dies upward
and downward, but withdrawn from the dies as the dotted positions indicate.
Since the motion of the links m and n, around the points o and o¹, is very slight,
the distance off the die is also very slight, yet if the hammer swayed perceptibly

page_text: off the die there would be a fin produced on the bolt head from the metal
squeezing between the hammer and the die, but with a sufficient length of links
this outward motion of the hammer is practically nothing. However, in order to
enhance the efficiency of my invention I have shortened the lower link, as shown
in Fig. 7, and whilst the link n', moves in a circle x1, x, x³, with the centre o³, and
whilst the longer link m², moves in the circle y¹, y, y, around the centre o³, the
end u, of the hammer will move in a curve z, z¹, w, u, v, z³, z³ and 2, of which
curve I practically ascertained the several points ¹, u, vand 2, by placing the
links m¹ and n¹, in four corresponding different positions. This curve when the
proportions of the links are properly adapted to the case, is practically straight for
a certain portion of the movement.
In Fig. 7 the curve is practically straight from u to v, and if the point u, is the
end of the hammer, as in Fig. 1, it is evident that u, or the end of the hammer is
moved for an ample distance in close contact with the dies d and d¹. Points o*
and o³, Fig. 7, correspond with the fulcrum pins o³ and o³, Fig. 1. Points x and y,
of Fig. 7, correspond with points x and y, of Fig. 1, and as do links m¹ and n¹, of
Fig. 7, correspond with links m¹ and n¹, of Fig. 1.
The motion of these points x and y, is so very slight that they may be with
safety run in water and scale without being materially injured, but they are readily
protected by the fenders or shields 8, Fig. 1.
To prevent lateral motion of the hammer guide, I make the jaws for the pins <
and y, very broad, as shown in Fig. 5, whilst the long fulcrum pins o' and o³,
pass through the frame A, of the machine, whereby they receive a wide steady
bearing.
I have not shown my improved hammer guides applied to the other hammers, as
they are not exposed to such an extent to the wear and tear that the lower hammer
slide is subjected to as to render their special protection necessary, but it is obvious
that each of the hammers in the spider may be operated in the improved way
described for the lower hammer.
While the above description of my invention and the drawings forming part of
the same show my present improvements applied to a bolt heading machine in
which the four lateral hammers are operated from the header, I do not confine or
restrict the use of my improved hammer guide to such particular construction of the
machine.
I have represented the machine on Sheet 1, with all the improvements above
described, and also those which remain to be described and represented in detached
views on Sheets 5 and 6.
Fig. 9 is a section on line y¹ and y¹, of Fig. 1. Fig. 10 is a section on line
and z, of Fig. 9. Fig. 11 is a front view of the die carriage, with die holders and
dies in position. Fig. 12 is a top view of the die carriage. Figs. 13 and 14 are
detached side views of the mechanism for operating the die carriage. Figs. 15
and 16 are rezpectively side and top views of that portion of the machine which
contains the die carriage.
So far, I have contined myself in this description to the improvements in the
working parts of the machine, particularly the hammers and their mode of
operation, whereas the following description of my invention relates to the other
parts and features of the machine, for instance, the dies for holding the bolt
blanks, their adjustments relative to the header, their mode of operation, and the
opening of the same, as hereinafter more particularly and fully set forth, and
represented in the drawings.
For convenience of reference, I shall continue as hereinabove to allude to the
several parts by assigning, to them such names as have been introduced and are
recognized in general practice, and for a better understanding of the nature of my
invention, I will introduce a few remarks relative to the present construction of
machines of this character.
Bolt heading machines as have heretofore been constructed, comprise two
separate and distinct classes. First: That class in which the dies have a fixed

page_text: position in the machine, and which, therefore, require a stoppage of the header
after the completion of each bolt, to allow of the insertion of a new blank between
the dies.
Second: That class of machines in which the header has a continually recipro-
cating motion imparted to it and in which the dies are mounted upon a movable
die carriage, susceptible of being moved a sufficient distance away from the header
to permit of the insertion of a new bolt blank between the dies and afterwards
moved in the direction towards the header again close up to the side hammers and
to lock it there so that the hammers may operate upon the inserted blank.
The disadvantages of the first class of these machines have long been recognized,
consisting principally in the sudden jar and wear and tear of the machinery upon
starting the header arising from being compelled of necessity to start the machine
anew after the insertion of each bolt blank.
The second class has been also more or less imperfect, for the reason that the
centre of the bolt blank, which is necessarily the centre of strain, in the beading
operation always occurred some distance above the centre of resistance, which
locked the die carriage in this position, and thereby produced a leverage tending to
lift the carriage from its seat during the beading operation, and likewise causing
an unpleasant vibration of the machine, proving more or less destructive to the
accuracy of the bolt.
This difficulty I have overcome entirely by laying the centre of force, required
for heading, and the centre of resistance in the same plane.
Another feature of my invention consists in the mechanical combination of
devices whereby I an enabled to move the die carriage with the dies to and from
the hammers without any great effort on the part of the attendant.
It may be here mentioned that some of the mechanism may be dispensed with in
small machines, the drawings, to be hereinafter more fully explained, refer parti-
cularly to machines for larger class of work.
In Figs. 10, 11 and 12, d and d' are the blank dies. These dies are made from
pieces of steel so shaped as to fully surround the blank when closely pressed
together, and are mounted on slides 11, which are in turn guided in guides 12,
forming part of the die carriage D¹, and held in position thereto by means of
caps 13.
When the bolt blank b¹, is in position to be acted upon, that is, gripped
by the dies d and d¹, the end opposite the one where the head is to be formed,
rests against an adjustable abutment screw 14. This abutment screw 14, being
located exactly in the centre of the bolt, and consequently in the centre of the
strain put upon the machine during the heading operation, has been the principal
element heretofore forbidding the introduction of a locking device for the die
carriage, whereby the die carriage might be locked central with the bolt. I over-
come this difficulty and lock this die carriage in position by means of a bifurcated
wedge 15, which straddles the blank abutment, as shown in Fig. 9.
This bifurcated wedge 15, rests against the frame A, of the machine, and locks
the die carriage D', by means of the tapering faces pressing against the steel
abutments 16, (Figs. 10 and 12,) of the die carriage D¹, and their situation is such
that the pressure of the header against the dies d and d¹, is transmitted in the
same horizontal plan with these abutments and against the wedge, thereby.
obviating the production of leverage which tends to lift the die carriage off its seat,
This has never before been accomplished, because the locking device has been in
all cases either a small crank connected with the die carriage below the centre of
the bolt blank moving the carriage into position and locking it when on its centre,
or it has been accomplished by means of a single wedge entering the die carriage
but partially remaining below the centre of the bolt blank. In all cases, however,
leverage has proved unavoidable, which is now entirely overcome.
Another feature of my invention embraces mechanism and combinations thereof
for holding the bolt blank and gripping it firmly during the heading operation, and
it embodies in conjunction there with certain devices by means of which the centre

page_text: of the bolt blank may be readily and effectively adjusted to a central position with
the header.
As above mentioned, the blank dies d and d', are mounted on slides 11, which
slide in guides 12, forming part of the die carriage, and are held in position by
means of caps 13. Each die holder slide is provided, at the end opposite the die
holding fork, with a toggle joint 17. These toggle joints are respectively jointed
to movable blocks 18, Fig. 11, rigidly secured in recesses of the arms 19, which are
continuations of the guides 12. At the end of these arms are set screw blocks 20,
provided with set screws 21. The functions of these screws being to move the
wbole system of blocks 18, with the toggles 17, and die slides 11, together with
the dies d and d¹, horizontally at will, until the required position is obtained.
The established practice has heretofore been to pack behind these dies a varying
number of layers of tin, more or less behind each die, and shifting the tin plate
from one to the other until the centre of the die occupied a central position with
the header. This operation not only required a stoppage of the machine for its
performance, but necessarily required the consumption of a considerable amount of
time for the setting, which in actual practice has proven not sufficiently accurate
for general work.
In order to open and close the dies d and d³, I connect the toggles 17, by means
of a link 22, with one arm 23, of bell crank, having its fulcrum 24, in the frame 19,
forming part of die carriage D¹, whilst arms 25, are provided with rollers 26,
which move upon the surface of the cams 27. These cams consist of one portion,
almost parallel with the centre of the machine, and another portion converging
rapidly backwards towards the centre of the machine. When the die carriage
moves in the direction of the arrow, Fig. 12, the bell cranks, which have their
fulcrums 24, upon the arms 19, of the die carriage, move with this carriage, and
consequently rollers 26, pass over the parallel portions of cams 27, which are
fastened to the main frame of the machine and remain stationary. During this
portion of the movement the dies remain in their closed position. When the die
carriage moves further the rollers 26, actuating the bell cranks are forced to
follow the inclined portion of the cains 27, by means of a pair of counter-cams 28,
parallel with the cams 27, and when the die carriage is in its remote position from
the hammers the dies are fully opened by the action of these bell cranks, acting
upon the toggles connected with the die holding slides: On the other hand, when
the heated blank is placed between the open dies and the die carriage D¹, is moved
forward towards the hammers, the dies will partially close as the rollers fastened
on the end of the bell cranks mount the inclines of the cams 27, and when the
rollers have reached their greatest height, the dies are closed, but, however, in this
position of the bell cranks the die carriage is only midway in the direction of the
hammers. For the other portion of the forward movement of the die carriage D¹,
the cams diverge slightly from the centre of the machine, which serves to give a
powerful grip to the bolt blank, aided by the favorable position of the toggles,
which are straight, when the die carriage is all the way up. When the die
carriage is in its operative position the blank is held so firmly that a minimum
amount of material will flow between the dies when the blank is upset and is being
operated upon by the hammer, thereby obviating one of the most common faults
existing in bolts made in open die machines.
A further important feature of my invention consists in the mechanism and
combinations thereof for moving the die carriage automatically. Here it may be
mentioned that the automatic movement is only adapted for large machines, whilst
I have practiced to work the die carriage by a pulling wedge with a foot lever and
by moving the carriage itself by a hand lever, yet for large machines, where the
parts are more ponderous and the travel much greater than in small machines, the
automatic mechanism is preferable, and it consists in devices for pulling the wedge
and subsequently moving the carriage, and so arranged that the carriage may
remain unlocked for an indefinite length of time for the reception of a new blank,
or it may remain locked during the heading operation, or during such period of

page_text: time as may be required for the different sizes and kinds of bolts, at the option of
the attendant in charge of the machine.
Machines have been constructed in which the heading, opening and closing, are
all automatically timed. This, however, I desire to avoid, as it is inadequate for
bolt works, due to the variety and character of the work done and the irregular
heating of the blanks, which cannot well be avoided.
The mechanism for producing the desired result will now be described :—
The bifurcated wedge 15, is held in its position and locked, by means of a
spring 29. A lever 30, (Fig. 10,) mounted upon a shaft 31, engages with the
same, while a second lever 32, (Figs. 14 and 15,) mounted on the same shaft, is.
actuated by means of an eccentric on the main driving shaft of the machine
through mechanism commonly called the Corliss trip mechanism, whereby the
bifurcated wedge can be moved at the option of the operator, as follows: When
the operator moves the lever 33, backward, that is to say, in the direction of the
arrow, the cam 34, will permit the crow's claw 35, resting on the cam 34, to drop a
sufficient distance to allow the trip mechanism to engage with the lever 32, as is
well understood by those familiar with the Corliss engine and thus eventually pull
the wedge downward. On the opposite side of the machine is similar mechanism,
also connected to the main driving shaft, in a manner as will be readily understood,
which is put into operation, acting through the lever 40, fitted to the shaft 41,
upon a toothed sector 36, and rack 37, by the action of a cam 39, fitted with the
cam 34, on one common shaft 38, and both cams so timed relatively to the header
and to each other that the wedge is released just before the header delivers its blow
upon the bolt head endwise, that is to say, when all the side hammers are clear of
the bolt head. Immediately after the wedge is drawn, the die carriage D¹, moves
backward, the dies open and the finished bolt drops out.
When the dies are to be closed, the operator moves the hand lever 33, in the
opposite direction to that of the arrow, thereby releasing the trip mechanism
actuating the wedge, at the same time reverses the action of the trip motion
actuating the toothed sector 36. Now the carriage is moved towards the hammers
having the new blanks in a gripped position, when at the same time the header is
moved, by virtue of proper timing, in the same direction, thereby permitting the
blank to move up between the side hammers. When the die carriage is in the
desired position, the bifurcated wedge 15, springs in position through the action of
the spring 29, and locks the carriage.
As
Fig. 13, illustrates the double acting trip mechanism for opening and closing the
dies, or, what is the same, for moving the die carriage forward and backward.
it will be seen from this figure, the trip 42 is double acting and according to
position of the cam 39, will either engage with the lever 40, when moving in the
direction from right to left, or vice versa, or not at all, when in a central position.
Spring 43 has for its object to keep lever 30, always in its upper position when
disengaged from the trip 35.
Spring 44, in connection with counterweight 45, has for its object to actuate the
cam 39, in case the operator has, (as he always does,) operated lever 33, and locked
it in the notch 48, regardless of time.
Having now particularly described and ascertained the nature of my said
invention, and in what manner the same is to be performed, I declare that what
I claim, is-
First. As an improvement in bolt heading machines, the hereinbefore described
manner of guiding one or more of the lateral hammers by a system of links, thus
dispensing with sliding guide surfaces, as and for the purposes specified.
Second. The combination in a bolt heading machine of a hammer guide, with
two vibrating guide links, substantially in the manner and for the purposes
described.
Third. The combination of the hammer guide G¹, links m¹ and n¹, toggles T',
rod R¹, lever F¹, and header H¹, substantially as and for the purposes described.

page_text: Fourth. In a bolt heading machine, the combination of the reciprocating header
with the crank shaft under the arrangement of mechanism substantially as described,
for taking up lost motion resulting from wear of the parts involved.
Fifth. The combination with the header H, and crank shaft D, of link L,
knuckle joint k, b, guide E, and adjustable rods r and r¹, aubstantially as and for
the purposes described.
Sixth. The combination with the header and the two pairs of lateral hammers.
of a link motion system substantially as described, whereby the header moves the
lateral hammers, substantially as and for the purposes set forth.
Seventh. In combination with the header H, the link motion system F, ƒ, ¿, R,
toggle T, and lateral hammer guide G, substantially as and for the purposes
described.
Eighth. In combination with the header H, the link motion system F1, f¹, R¹,
toggle T¹, and lateral hammer guide G¹, substantially as and for the purposes
described.
Ninth. In combination with the header H, the link motion system F2, fƒ³, R³,
toggle T, and lateral hammer guide G2, substantially as and for the purposes
set forth.
Tenth. In a bolt heading machine, a movable die carriage, locked in position by
wedges entering the die carriage up to or beyond the centre line of the bolt blank,
as and for the purposes described.
Eleventh. In a bolt heading machine, a movable die carriage, provided with
guides for the die holders, in combination with the die holders, the latter being
connected to toggles, adjustable in arms of the die carriage and operated by a lever
pivoted to the die carriage and actuated by end wise motion of the die carriage
through cams having a fixed position on the bed of the machine, as and for the
purposes described.
Twelfth. In a bolt heading machine, the movable die carriage D¹, in combination
with the die holders 11, bell cranks 23 and 25, cams 27, and counter-cams 28, so
arranged as to hold the bolt blank during one portion of the endwise motion of the
die carriage, and releasing the blank during the remaining portion of its movement,
substantially as and for the purposes described.
Thirteenth. In a bolt heading machine, the combination of a movable die
carriage D¹, bifurcated wedge 15, with springs 29, lever 30, shaft 31, hand lever 33,
cam 34, sector 47, pinion 46, trip mechanism 35, and main driving shaft D, sub-
stantially as and for the purposes described.
Fourteenth. In a bolt heading machine, the combination of a movable die
carriage D¹, with rack 37, segment 36, shaft 41, lever 40, double acting trip
mechanism 42, main driving shaft D, cam 39, shaft 38, pinion 46, segment 47,
lever 33, spring 44, and counterweight 45, substantially as and for the purposes
described.
Fifteenth. In a bolt heading machine, the mechanism for moving the die carriage,
consisting of lever 33, spring 44, segment lever 47, pinion 46, cam 34, shaft 38,
cam 39, trips 35 and 42, operated from the main driving shaft D, all arranged in
proper succession as and for the purposes described.
In witness whereof, I, the said Ferdinand Philips, have hereunto set my hand
and seal, the 28th day of November, in the year of our Lord one thousand
eight hundred and eighty-five