Year: 1886

page_text: I, WILLIAM ROBERT LAKE, of the firm of Haseltine, Lake and Co Patent Agents,
Southampton Buildings in the County of Middlesex do hereby declare the nature of
my 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 particularly relates to hand-rock-drilling machines in which are
combined a series of reciprocating hammers arranged to revolve in concert about a
common centre, each being successively brought into a line with the drill tool, and,
after being first forced back by cams against a spring, released to deliver its blow
upon the head of the drill tool, the drill tool itself revolving about its own axis
through a portion of a revolution, between the hammer blows.
The invention herein described consists in the following improvements, all being
combined to reach a common end, that is to say :-
In a method of connecting the drill tool with the machine, dispensing with the
ordinary drill clamp.
In the arrangement upon a revolving frame of a number of sector shaped
hammers, each having a helical cam forming an integral part of it, and a series of
rollers mounted upon the inside of the enclosing case of the machine in a helical
curve forming a cam-way, which, acting in combination with the hammer-cams,
produce the required rotation of the hammer-frame. This construction permits the
hammers to be made of a single solid piece of metal.
In the arrangement of the hammer driving springs, whereby all friction upon the
surrounding parts is avoided.
In the addition of an improved device for holding the hammers in place after
the compression of the helical driving springs, and controlling their release, thereby
ensuring accuracy and rapidity in the delivery of the blows, and the greatest
possible freedom from wear and tear.
In the arrangement of parts whereby the hammer springs are distended when
the machine is at rest.

page_text: In the improved construction of the friction rollers attached to the inside of the
enclosing case and acting as a cam-way to drive the hammers, whereby they are
rendered self oiling and nearly frictionless.
In an improved automatic feed which adjusts itself perfectly to the work to be
performed, and is thrown in or out of gear at pleasure.
In an improved device for causing the intermittent rotation of the drill tool.
In an improved construction of the frame of the machine, whereby it acts as an
enclosing case to protect the working parts from dust or accidental injury; which
frame is provided with openings for examination and lubrication.
In an improved device for attaching the machine to its supports, so that it can
be readily and safely connected and disconnected as occasion may require.
In a device whereby the drill can be instantly withdrawn from the bore, and as
quickly brought again into position without altering the axial line of the work.
In a device whereby the path of motion of the crank arms is always in a vertical
plane whatever may be the position of the primary support or column; which is a
matter of great convenience in working.
In certain improvements in the general construction of the elevating and
depressing devices, and in an improved construction of the clamp for connecting
the machine with the supporting column.
In addition to the above stated improvements there are many minor features of
improvement.
The whole machine may be briefly described as consisting of a suitable support
having adjustably secured to it, by an improved clamping device, a sleeve in which
a tubular case containing the drill operating mechanisin can slide forward in a
uniform direction under the action of a feed-screw, operated so as to automatically
adjust itself to requirements of the work.
Within this enclosing and protecting case or shell, as I call it, are arranged, on
the angles of a cross-shaped core frame, four reciprocating hammers of such cross-
section that the hammers and frame, fitting compactly together, form a cylinder,
through the centre of which a rod passes, which acts as a feed regulator. The
frame itself connects directly by means of a four-toothed cam gearing with a spur-
wheel on the drill socket, and rotates the drill tool, between the successive hammér
blows, through a small portion of a revolution.
The hammers are actuated by helical springs, and are drawn back against the
retractive force of these springs by the rotation of a crank-shaft operated by hand
and transmitting its motion through intermediate gearing to the hammer-frame,
which rotating with its hammers forces certain cams on these hammers into contact
with rollers_set helically on the inside of portions of the enclosing case. These
portions are hinged for convenience of removing cleansing or oiling the rollers, and
for other purposes which will be hereinafter more fully set forth. Theso_gates
are provided with a secure and easily operated locking attachment which I also
describe in another place.
The hammers are held, when not in a proper position to strike a blow, by
notches in their ends, in combination with a system of roller-bearing spring levers
or triggers which are withdrawn at the proper instant by the revolution of the
hammer frame itself by means of a cam fixed to the shell or enclosing case.
Other cams enable the hammers to pass over the head of the tool and assist the
cams which force the hammers to compress their driving springs.
The whole machine is so constructed that it can be elevated or depressed and
operated at any angle vertical or horizontal with the crank shafts in the most
convenient position.
There are no loose nuts or bolts; the oiling is principally done by merely putting
a quantity in through the opening of the gate and allowing it to distribute itself by
the shock of the haminer blows. The drill tool can be removed and reinserted at
will without interfering with its perfect alignment.
The automatic feed can be thrown out of gear and the tool fed forward by hand
or withdrawn at pleasure by a very simple operation.

page_text: In the description of the figures of the drawings "front end" means the end
carrying the drill tool, and "rear end" the opposite end.
In the said drawings:
Figure 1 is a perspective view of the complete machine mounted upon its
supporting column ready for use with the gates of the enclosing case thrown open.
Figure 2 is a side elevation of the complete machine mounted upon its column.
Figure 3 is a top view of the complete machine.
Figure 4 is a longitudinal vertical section of the whole machine.
Figure 5, is a cross section on line X X of Figure 4, shewing the tubular shell or
enclosing case, the revolving hammer frame, and the hammers.
Figure 6 is a cross section on the line X1, X' of Figure 4, shewing the gates of
enclosing shell, the locking device, the revolving frame, and the hammers in section
at the point where their driving springs are placed.
Figure 7 is a rear view of the machine after removing the box containing the
driving mechanism, this view is nearly on a line with X*X* Figure 4.
Figure 8 is a longitudinal section of the middle portion of the outer enclosing
case or shell, showing the cam rollers upon one of the gates which is shewn closed
and locked.
Figure 9 is a front end of the complete machine attached to its supporting
column.
Figure 10 is a rear end view of the complete machine and column.
Figure 11 is an elevation of the clamp bracket and column.
Figure 12 is a front view, of the clamp bracket and column.
Figure 13 is a plan view of the same parts.
Figure 14 is a vertical cross-section of the same on the line X3 X³ of Figure 13.
Figure 15 is a rear end view of the sleeve.
Figure 16 is a side elevation of the sleeve.
Figure 17 is a longitudinal vertical section of the sleeve on line X* X' of
Figure 15.
Figure 18 is a longitudinal section of the lower part of the sleeve in the same
plane as Figure 17 but shewing more in detail the method of fastening the feed nut
to the sleeve.
Figures 19 and 20 shew in detail the locking device, for securing the feed-nut in
the sleeve. In Figure 19 the thumb piece is turned around unlocking the latch
which secures the feed-uut; in Figure 20 the latch is turned back entirely
releasing the feed nut.
Figure 21, is a side elevation of the middle part of the enclosing case or shell,
with the gates open and thrown down, and the locking device thrown back.
Figure 22 is a vertical cross-section through the gates on the line X³ X³ of
Figure 21.
Figure 23 is a vertical cross-section of the driving gear box through the axis of
the driving shaft.
Figure 24 is a vertical longitudinal section of this same box.
Figure 25 is a vertical longitudinal section of the lower part of the machine
shewing in detail the feed screws, feed nut and the mechanism of the hand feed.
Figure 26, is a cross-section through line X X' of Figure 25.
Figure 27 is a detail view of the thumb piece at the rear end of the feed screw.
Figure 28 is a detail view of the cam-bush at the end of the feed screw.
Figure 29 is an end view of the same.
Figure 30 is a rear end view of the revolving hammer frame with the driving
gear removed, shewing more particularly the position of the four trigger levers
which act to retain and release the hammers, the corresponding retaining and
releasing pawls are also shewn in this figure, all the hammers are held in place.
This
Figure 31 is a view of the same parts shewing the position of the trigger or
roller bearing lever and its pawl when acted upon by the releasing cam.
figure is a repetition on a larger scale of Figure 7. in both figures the direction of
rotation is indicated by arrows.

page_text: Figure 32 is a vertical longitudinal section through the rear part of the revolving
hammer frame on a line X7 X' of Figure 30 shewing more in detail the action
of the retaining and releasing pawls, and the hammer actuating springs of the
hammers, in this view one hammer is shewn held by its trigger and the other,
· released and forced forward by the action of its helical driving spring which is
removed for greater clearness in the figure.
Figure 33 is a precisely similar partial section but shewing the trigger in the act
of releasing a hammer.
Figure 34 is a repetition of Figure 33 shewing more particularly the position of
the pawl immediately after the release of hammer.
Figure 35 is a longitudinal axial section of the rear part of the revolving
hammer frame on line X3 X' of Figure 30, shewing more particularly the con-
struction and position of the automatic clutch.
Figure 36 is a front end view of the box containing the drill rotating devico.
Figure 37 is a cross-section on the line X10 X 10 of Figure 38 of the drill socket
and spur-wheel, and the four-toothed cam which rotates this socket, in their
relative positions at the time of first contact.
Figure 38 is a longitudinal section, of the drill socket and the cam for rotating
the socket on a line Xº Xº of Figure 36.
Figure 39 is a cross section of the drill socket cam, shewing their relative
positions at the time of first contact.
Figure 40 is a cross section of socket and cam, shewing the relative positions at
the moment of last contact.
Figure 41 is also a cross section of cam and socket, shewing the socket at rest,
and the cam in the middle position between last and first contact.
Figure 42 is a face view of the cam-plate in the front of the machine for
preventing the outer ends of the hammers from striking against the end of the
drill tool while being rotated past it.
Figure 43 is a development of the curves of the cams upon the cap Figure 47.
Figure 44 is a rear end view of one of the hammers.
Figure 45 is a plan view of one of the hammers This is the outside convex
face of the hammer.
Figure 46 is a side elevation of one of the hammers.
Figure 47 is a longitudinal section of a hammer.
Figure 48 is a front end view of a hammer. This is the end which delivers the
blow upon the tool.
Figure 49 is a top view of one of the roller plugs which are inserted in the gates
of the outer frame to form a cam course for compressing the hammer springs.
Figure 50 is an axial section of the roller plugs and cam roller on a line Y Y of
Figure 49.
Figure 51 is a side view of the roller shewn in section in Figure 55.
Figure 52 is a plan view of the flanged plate at the base of the roller.
Figure 53 is a vertical section through line Y¹ Y¹ of Figure 52.
Figure 54 is a plan view of the thrust plate at the top of the roller.
Figure 55 is a section on line Y' Y of Figure 54.
Figure 56 is a vertical axial section of the roller stem.
Figure 57 is a plan view of the presser foot which is used in the automatic feed
and is shown in its proper position in Figure 43.
Figure 58 is a longitudinal section of this presser foot on line Y³ Y³ of
Figure 57.
Figure 59 is a cross section of the presser foot and,
Figure 60 is a perspective view of the presser foot.
The principal parts are as follows:-
A, is the supporting column; B, clamp for attaching the machine proper to its
sunnorting column CD bracket and stren wonentialu in which slave 7 in hold.

page_text: smaller cylinder I enclosing the feed-screw N, placed below the principal cylinder
and parallel with its axis; G, tubular feed-nut secured to E; H, H, gates carrying
cam wheels U operating hammers, T I, case of feed-screws; L, box containing
crank shaft for rotating the machine and tool; M, crank shaft for driving machine
N, feed screw working in the feed nut G; O, box or case containing drill-tool-
rotating-device; P drill tool; R, hammer frame; S, drum containing locking and
releasing levers for the hammers; T, hammers; .Ü U, rollers set in gates H, H, and
forming a cam way on inside of gates H, H, to operate hammers; V rod for con-
necting rotating mechanism of drill tool with driving or crank shaft, M. X, X,
Y, Y, all indicate line of sections.
The functions to be performed by the various parts and combinations of parts
used in this machine may be summed up briefly as follows:-
First. Devices for attaching the machine to its supporting column so that it can,
as a whole, have the following motions:-
A motion of translation, which in the ordinary position of the machine,
consists of elevation and depression upon its supporting column.
An angular displacement of its axis in either or both horizontal and vertical
planes.
Rotation around its own axis.
A pivotal motion about a line parallel with its own axis, but not coincident
with it.
A freedom to move, when actuated by the proper mechanism, back and forth
in its own axial line.
Second: Devices for protecting the operating parts from dust, retaining the
lubricating material, and permitting ready examination of parts when required.
Third Devices for rotating the frame carrying the hammers and bringing them
successively in front of the tool, and at the same time compressing the hammer
driving springs.
H
:
Fourth Devices for locking the hammers when they are forced back against
the resilience of their motor springs and releasing them to give the blow.
Fifth Devices for producing a slow and intermittent rotation of the tool about
its own axis.
Sixth Devices for automatically feeding the whole machine forward in its own
axial line just in the proportion that the tool advances into the rock; and in con-
nection with this automatic feed, a device for throwing it out and permitting of the
withdrawal of the machine or the operation of the feed by hand.
These various functions will be considered as far as possible in their regular
order.
The machine herein described can be used with any of the supporting devices
known to miners, such as tripods, beams &.
In the present case the machine is attached to a column A by means of a
clamp E.
This clamp consists of a ring B forming the body or principal part and three
arms; two of which 62 63 are flexible but integral with B, while the third b, is
rigid and pivoted to B by means of two lugs b³ the end of b is slotted to receive
the bolt hinged to the outer ends of the two arms 62, 63, and pressing when
required against the end of the arm b by means of the nut b³.
It is obvious that by turning the nut 6 in the proper direction the three
arms, b² b³, b will be made to press tightly upon the column A, holding the clamp
firmly in place, the flexibility of two of the arms permitting a more secure hold
apon the column.
A ring and set-screw can be placed beneath the arms of the clamp to support the
machine when the nut 65, is released.
This clamp permits of the adjustment of the machine to any horizontal angle.
The body B, of this clamp is ring-shaped and its circular opening is offset upon
both sides leaving a shoulder or flange 66, (see Figure 14), the bracket C, fits into
one offset, and the plate c, into the other, these two parts are made to tightly clasp
.

page_text: the ring of clamp B by a stud c² and a pin c³ both fastened to the base of bracket C
and fitting through holes in the plate c. The plate c and bracket C being thus
held together can be made to revolve in the recesses or offsets of the ring B, and
can be firmly fixed in any desired position by screwing down the nut c* of the
stud c², which causes the bracket and plate to firmly clasp between them the
shoulder be of the clamp B and tl.us by the great friction developed hold the bracket
and the machine attached to it in any required position. This gives the adjustment
for vertical angles.
A strap D, is pivotted at the bottom by means of the lugs c³, and a pin d to the
bracket C, (Figures 9, 10 and 14) it is kept from turning upon its hinge by a 1
clever c³, pivoted by a screw-bolt c', to the bracket C, and locking the strap D, by a
recess cut in the underside of the lever c fitting a corresponding projection or
lip d upon the strap D.
In order to securely lock the lever c in its place and prevent it from moving
away under the effects of the vibrations of the machine a pin c placed in the 1
centre of the handle of lever c, and pressed forward by the action of the spring c³
fits into a small recess cut in the outward face of lip and causes sufficient
resistance to the movement of the lever to keep it in place, unless forced out by
the application of power to the handle.
-
The strap D, is made in two parts held together by means of the screws d³, and
the stud and nut d', and is borrowed to receive the sleeve E which rests easily
on it.
D, is put together in this way so that it can be fitted into the
sleeve E.
groove
in
The sleeve E, is also made in two parts held together by screws e and is provided
outside at its middle with two flanges or projecting rings e², e, between which is a
groove leaving a cylinder of the proper diameter to fit the bore of strap D, in which
it can turn but is fastened at any point by tightening the nut dª causing the strap
to tightly clasp the sleeve.
The revolution of the whole machine about its own axis is obtained by turning
the sleeve E, in strap D.
The interior of sleeve E is bored and planed to fit the tubular shell F, of the
machine; and on its under part a recess, is bored in a line parallel with its axis to
receive the forward end of the feed nut G; this being its bearing upon the
stationary part of the machine.
The feed nut is held in its recess by the latch g, pivoted at G to E, and passing
through a slot cut in the sleeve fitting over the feed nut and into a recess cut
therein. To keep this latch in place in any position of the machine and to hold it
securely it is made to lock by a thumb piece e, or lever g³ pivoted to g, and having
its pivot provided with a projection g, fitting a recess in the sleeve E, when the 4
piece g³, is turned so that it covers the latch g. For details of these parts see
Figures 15 to 20 both inclusive.
The thumb piece g³, having been folded over latching as shown in Figure 15, tho
projection g¹ engages in its recess in sleeve E, and prevents the latch from leaving
its place in the slot and groove above described.
To disengage the latch g the piece-g³ is first caused to revolve upon its pivot or
bolt g³ until it reaches the position shown in Figure 19; the projection having thus
been removed from its recess in sleeve E, the latch itself is made to turn upon its
ping and is thus withdrawn from its seat in the slot of E, and groove of feed nut,
leaving the latter unfastened as in Figure 20.
The notch in the latch g firmly grasps the feed nut G, when the latch is locked
in place, and prevents the rotation of the said nut G, when at work.
4
E
The whole working mechanism of the machine is completely enclosed in a
tubular shell or case F, the front end F³, of which is evenly planed to fit the bore
of sleeve E, and slide freely in it under the action of either the automatic or the 5
hand feed devices,
,

page_text: Immediately in the rear of the shoulder separating this planed part from the
other end are two covers or gates H, H, hinged upon pins h, and opening outward
and in the usual position of the machine downward.
The gates H are fitted closely into the openings made to receive them and bear
at their upper end upon the shell F they are locked by means of the cover h³,
pivoted at h³, to the shell F, and having the flanges h, which fit over the flanges h
projecting from the gates H where they meet. At the forward end of the
cover a hole is drilled to receive the bolt ho, having the projection h made to fit
a recess cut in the shell F. On the upper end of the bolt he is fastened a thumb.
piece hº.
The action of this locking device is very similar to that shown and described to
lock the feed nut.
When the thumb-piece h³ is turned as shown in Figure 21, the cover can be,
lifted up as shown, the thumb piece assisting the operation by adding length to the
leverage of the cover h².
When the cover is raised the gates can be opened. To lock them they are
brought together the cover h² turned down upon them, and the thumb-piece which,
has been kept extended outward during this first part if the operation turned over the
cover h³ bringing the projection h' of bolt he into its recess and locking the device.
On the under rear part of the shell F and in a line parallel to its axis is a
cylindrical projection I, bored out to receive the long cylindrical feed-nut G, which
is fastened at one end to the sleeve E, by a latch g, previously described.
At the rear end of the shell F and secured to it by three screws 7, l, is a box L,,
holding the driving shaft M and other devices.
The tubular arm 12, receives the shaft M which rests at its other end in the cap l³
which is screwed to the box L.
The cap, is made removable so that the bevel wheel m can be inserted into the.
box L. The bevil wheel m is keyed to the driving shaft H by a pin shown but
not lettered. The ends of the driving shaft are made square to receive the driving
cranks M. For details see Figures 23 and 24.
A steel pivot, is secured by screws 15, to a portion of the internal framework
of driving box L, in such a position that it is directly in a line with the axis of
the machine and at right angles with the driving shaft M.
At the lower part of the box L, extending several inches in the rear is a tubular
projection corresponding with projection of shell F, and bored out to receive the
tubular feed nut G.
The hammers T are carried by a revolving frame R which is a tube from which
radiate four ribs.
In these ribs, recesses are planed to receive and hold the hammers T.
The frame R turns in front, upon the journal of the cam which rotates the drill
tool and in the rear by the hardened steel pivot l, fitting into a journal box, in the
bevel wheel m³.
The frame R and with it the hammers is caused to revolve of means of a bevel
wheel m³ gearing with the bevel wheel m which is pinned to the driving shaft M.:
See Figures 32, 33, 34.and 35.
Looking now at Figure 35, the bevel wheel m², is shown secured to a drum S,
by screws m³. The drum S is secured to the revolving frame R, by screws s; so
that bevel wheel m², drum S, and hammer frame R revolve together when the
crank shaft M is turned; and the hammers are successively brought opposite the
shank of the drill tool
In the centre of the bevel gear m³, a hole is bored to act as a bearing for the,
steel pivot and a hardened steel thrust plate, is placed at the bottom of the hole.
The hammers T, are solid steel bars having grooves planed upon their sides, to
make a dovetailed fit in the bearings planed upon the ribs of the hammer frame R:
The hammers must be slid into their places by introducing them endways.
Ore end of the hammers is solid and cut off square to deliver the blows; the
other end has a stem for the driving spring and a recess & between this stem

page_text: and the outside shell t³ covering the spring. A notch is made in the end of the
stem to, to lock the hammer in place when its spring is compressed.
A portion of a helical curve projects from the curvilinear face of the hammer
and acts as a cam forcing the hammer back against its driving springs when it
comes in contact with the rollers U, set helically upon the inside of the protecting
shell or case F.
When the hammers are placed in their beds upon the revolving frame R the
stem enters a thimble r secured to the drum S, and also said drum reaching as
far as the locking lever which will be more fully described hereafter.
The rollers above referred to, (see Figures 21 and 22) are so arranged that the
line of their centres describes a helical curving having a pitch of three inches.
. These rollers are placed at equal distances from the axis of the machine and are
separated by arcs of equal length.
The pitch of the cams upon the hammers corresponds with the pitch of the
rollers, and both rollers and cams have corresponding bevelled edges of contact.
The operation is as follows A movement of revolution being imparted to the
frame R, the cam t of one of the hammers comes in contact with the roller U, and
causes said hammer to move toward the rear of the machine and to do this it must
compress a spring to, placed upon the stem of the hammers and bearing against a
thimble secured to the front face of the drum S.
The length of the cam t being greater than the distance between the centres of
two consecutive rollers, the cam is resting on roller No 2 before it has left roller N° 1
and the same movement of translation of the hammer continues as the cam is
advancing upon each successive roller.
When the cam is about to leave roller N° 4 the hammer has moved toward the
rear of the machine to the full extent of its path in that direction, and the notch to,
at the end of the stem t has come opposite the spring trigger or roller-bearing-
lever, which carries at its end the freely revolving roller and this trigger
being pressed toward the axis of the machine by a spring 4, has lodged in the
notch . A helical spring to placed upon the stem t, of the hammer T, and guided
by the thimble t', in the stem of the hammer and another thimble t, on the flange
plate & attached to the drum S, has been compressed' during the backward move-
ment imparted to the hammer T; and the resilience of the spring causes the
trigger to press firmly into the notch to and securely lock the hammer, as shown
in the upper part of Figure 32.
Each hammer is thus successively locked they are in turn released to give their
blows by a number of levers &³, pivoted to the rear face of the drum s, and operated
by a stationary cam s on the inside of shell F. These levers press at one end
against the upper portion of the triggers 2 and at the other end are suitably
curved to act in concert with the fixed cam s*.
As the frame R, is revolved each lever is in turn brought opposite the cam 8*,
its outer end forced in, throwing its inner end into contact with the trigger ª and
thus pushing back the trigger 2 against its spring 7 and releasing its roller ³
from the notch in the stein of the hammer; the latter moves suddenly forward
under the action of its helical spring and delivers its blow; after the hammer is
released, the trigger is again pressed inward by its spring, and is ready to lock the
next hammer.
The rollers are placed at the ends of the triggers 2³ to lessen the friction and
wear of the parts in contact.
As I usually construct the machine the hammer actuating springs require a force
of 200 pounds to compress them to their full extent of two inches.
· All the hammers being actuated each in its turn, in the manner described; the
result of the movement given to the driving shaft M, is to cause the delivery of
hammer blows upon the tool P, held in a socket o10, the position of the fixed cam s,
which operates the lever a' and the triggers being such as to release the hammers
at the time of their passage in front of the socket.

page_text: Going a little more into the details of the construction of the drum; in the rear
of the flange & and fastened to it by screws is a cylindrical piece which I call the
drum; four holes in a line with the thimbles t8 (see Figures 32 and 38) are drilled
in this drum, and four recesses are milled out to receive the pivoted levers 7
bearing the rollers ³, these levers I call triggers and their function has been
previously described. These levers are pressed toward the centre of the drum by
the action of springs, attached to plates fastened to the drum.
The next important movement to be obtained is the rotation of the drill tool
itself, which must be in the interval between the delivery of two consecutive blows
of the hammers.
The devices which effect the rotation of the drill tool are enclosed in a box 0,
which is fastened by means of the screws o², (Figure 38), to the inside of the
tubular shell F, at its forward end.
A cap o³, shown in Figure 42 is fastened to the box O, by the screws o³, which
is provided with two cams o, o". These cams are shown developed in Figure 43.
07, is a four toothed cam provided with journals resting in the bearings bored
out for that purpose in the box and cap.
This cam is drilled throughout its length, the diameter of the hole in the rear
part being much larger than the one reaching the forward part. In the smaller
part of the hole is fitted the plunger o³ provided with the head oº.
Gearing with this cam is a socket o¹, provided with a square hole for the head
or shank of the drill-tool P, and resting in bearings in the box O, and its cap o
On the socket o¹º are eleven teeth. A pivoted pawl o¹¹, is pressed upon the teeth
of the socket o10, by the action of a spring o¹³.
When the cam o, is made to revolve continously one of its teeth comes in contact
with a tooth on the socket o⁰ as shown in Figure 39, and imparts to the latter a
movement of rotation which stops when the contact between the two teeth has
ceased, as shown in Figure 40.
The distance between two consecutive teeth on the cam o' being greater than
the distance separating two consecutive teeth on the socket 010, the motion of the
latter does not take place, until after an interval of rest. The momentum of the
revolving socket is overcome by the spring pawl oll, and this pawl stops it between
two teeth so that the shock from the blow upon the drill is not communicated to
the four toothed cam and its operating mechanism. This position is shown in
Figure 41. The two acting teeth, (Figure 39) being again in contact, the socket
revolves and then again. stops as explained above. Thus the continously revolving
cam o, imparts to the socket o, an intermittent rotary motion.
It will be noticed that the pawl oll, also prevents the retrograde movement of
the socket o7..
It now as regards the drill turning mechanism only remains to show the means
by which the cam o² is revolved.
For this purpose the front end of the frame R is provided with the stem V,
fastened to it by means of a pin ². This stem is drilled out through its whole
length and its forward end fits into the rear part of the cam o'. As the frame R
revolves, the stem V, revolves with it and turns the cam o' also; in this way every
complete revolution of the hammer frame causes 'the drill tool to turn through
about 1-10 of a revolution.
The lug v³, of the stem fits into a recess cut in its edge of cam o², connecting the
frame R and the cam together.
The centre of the drum is bored out and is properly slotted to receive a clutch 2³
best shown in figure 35.
This clutch is composed of a cylindrical body fitting the bore in the centre of
the drum S, with a flat projection sliding in a slot cut in the central bore of the
drum, and a slot is also cut in the bevel gear m³ which is a continuation of the
slot in the drum S, to receive the clutch

page_text: The clutch rº, is kept normally in contact with its recess in the wheel m³ by a
spring.
The automatic feed is accomplished by the following devices :-
The feed-nut G is a long hollow cylinder closed at its forward end by a plug go
provided with a groove made to receive the latch g, of which the operation has
been fully described.
The rear end of the feed nut is provided with an internal thread, and into this
thread is screwed the feed screw N. The feed nut G, passes through the pinion m*,
the tubular projection of the case L, the tube I and reaches the rear part of the
sleeve E where it is fastened.
The pinion on is fitted so as to revolve freely between the end of the tubular
shell F, and the rear driving gear box L and is provided with a long hollow
cylindrical hub m resting in the bore of 16 in box L. At the end of the tubular
part of box L is a cap n used as a bearing for the rear end of the feed screw N.
This cap n is screwed into the tube and locked by means of a spring and pin.
The feed screw N is provided with a collar n³, to bear upon the innerface of the
cap screw n. A second collar n³ is fastened to the screw by means of a pin and
bears upon the shoulder of the recess bored out to receive it thus forming an
external bearing.
The outer end of the feed scrow N is made square to fit a crank which can be
placed upon it when required.
At the end of the hub of pinion m³, is a recess made to receive the latch n^,
which is fitted into a slot cut in the feed screw and collar. The notch in the end
of the hub of pinion m³ occupies a considerable portion of the circumference.
The rear end of the feed screw N is hollow, and is provided with a plunger n³;
upon the stem of which is placed a spring no resting at one end against the inner
face of the bush n', at the other end upon the shoulder of the plunger itself.
The plungern and latch n are connected by means of a screw n³ passing
through a slot cut in the journal of feed screw N.
On the end of the stem of plunger n³ is, fitted a thumbpiece n³, held in place
longitudinally by the screw n¹º, but free to revolve on the stem.
This thumb piece (figure 27) is provided with a projection n¹, designed to bear
upon the rear face of bush n' (shown in figures 23 and 29).
'This face is cut in the shape of a cam so that by turning the thumb piece in the
proper direction, the action of the projection starting from the point n¹s, to
reach na, is to give the plunger n³, a movement toward the rear drawing with it
the latch and compressing the spring nº.
The withdrawal of the latch releases the hub of gear wheel m* from its con-
nection with the feed-screw and thus permits the latter to be operated by hand in
either direction by attaching a crank to the square end of the screw.
If the thumb piece is now turned in the opposite direction, the plunger and latch
will regain their former position, the latch n, entering the recess cut at the end of
the hub of pinion m², and locking the pinion and feed screw together.
For the purpose of operating the feed automatically a presser foot o¹s, shown in
Figures 57 and 58, and perspective figure 60, is placed in grooves cut in box o, and
its cap o². This presser-foot consists of a short hollow cylinder fitting round the
rear part of cum o' and provided with two projections which bear against the rear
face of the teeth of socket 010. A sort of handle runs from one side of the rear end
of the cylindrical portion of the presser-foot, and into a small hole in the centre of
this a rod Vs, enters, this rod V, passes down through the centre of the hollow stem
which rotates the cam o', and is connected at the other end with the clutch 7º at
the rear end of the machine. The rod V5, is kept pressed against the presser-foot
by a spring V6, bearing upon a collar V', fastened to the rod V³ and on a shoulder 'in
the bore of the frame R..
The position of these parts can be seen in fioure 4.

page_text: The presser of this spring Vo is transmitted to the presser-foot o¹³, and by it to
the socket and the drill-tool P, keeping it pressed against the face of the rock upon
which it is working.
Under the action of the blows the tool advances, the socket pressing upon its
shoulder, is followed by the presser foot o", and the rod V. This allows the rod V³,
to move forward and the clutch is pulled by its spring, into the notch in the
wheel ms, which is in gear with the pinion m', connected with the feed screw N,
by the latch n, causing the said wheel to drive the pinion m', and thus to actuate
the feed screw.
The machine then moves forward and the effect of this motion is
to separate the clutch from the wheel m, thus stopping the general forward
motion of the machine..
But the rock being continually attacked the tool advances and the presser-foot.
follows, allowing the rod to move forward and thus again connect the clutch to
the gear wheel m³ and turn the feed screw forward.
Thus the automatic forward movement of the machine is regulated accurately by
the progress of the drilling; the machine advancing rapidly when the boring is
rapidly done, or slowly when the progress of the drill is slow, or stopping altogether
if the progress is stopped.
I have explained before how by using the thumb piece n³, the automatic action
of the machine can be stopped and the feed operated by hand.
Having now fully explained the general principles of the action of the machine
I will describe several important details of construction.
While the machine is being used, three of the four hammer driving springs are
under more or less tension and one only is perfectly distended.
As it is desirable that all the springs should be without tension when the
machine is at rest, I have devised a certain construction to obtain this result.
By causing the frame to turn backward when the cams on the hammers T, pass
on the front edge of the rollers sending all the hammers forward and releasing all
the springs.
In order to allow sufficient room for this movement of release, the cap of box O,
is recessed in its upper part.
This cap o is provided with a cam-edge between the recess or opening just
mentioned and the socket o10, the highest point of the cam being at 0°. This is
done to guide the face or end of the hammer over the shank of the drill P.
Without this device, especially in downward drilling, the side of the hammer
would strike on the side of the socket, or the shank and prevent the working of
the machine.
On the other side of the socket o7, is a second cam edge placed there to receive
the end of the hammers and drive the same backward before its cain can come in
contact with the first of the cam rollers on the gates H.
The rollers U are constructed so as to retain their lubricating oil and keep the
same at the point where the strain is most severe. The details of the construction
of these rollers is shown fully in figures 50 to 56 both inclusive.
The pivot u of the roller U is made tapering and its stem u³ is fitted tightly and
pinned by a pin u³ in the shank of the hole in the steel plug ut. The roller is
provided with a plate us, made of hardened steel to receive the thrust of pivot u.
A second plate or collar 10, figures 50, 52 and 53, having a flange us, is fastened
by a screw u', at the opposite end to prevent the roller from leaving its pivot.
The flange u of plate u corresponds with a recess turned at the base of
pivot u.
An oil hole us reaches from the face of the roller U, to the base and into the
channel made by the flange us, figure 50.
A helical groove u is cut in the tapering hole or bearing of roller U, from the
oil hole us, to the thrust plate u³.
When the roller U is revolving, the effect of the groove is to cause the oil to.
low toward the thrust plate. When it is desirable to lubricate the rollers, the two

page_text: gates H are opened, so as to be as shown in figure 22, and a drop of oil is put in
each hole.
е
After this the gates are closed and when at work the roller distributes the oil as
above explained.
At the front end of the machine a nose W, projects and in this a hole is drilled
to receive a pin p, which by coming in front of the shoulder of the drill tool keeps
it in place when its position is vertical without the aid of any clamping device.
Having now particularly described and ascertained the nature of the said
invention and in what manner the same is to be performed as communicated to
me by my foreign correspondent I doclare that I make no claim to a rock-drilling
machine adapted to be operated by hand nor to a rock-drilling machine pro-
vided with rotating and reciprocating hammers actuated by cams but what
I claim is:
First: The combination of parts substantially as shown and set forth for the
purpose of drilling rock or similar material in which the blows upon the tool are
given by a series of hammers automatically reciprocating under spring pressure
parallel with the axis of the machine about which they also revolve, their nxes
always remaining parallel to the axis of the frame in which they slide, and their
reciprocation resulting from the said revolving motion in conjunction with certain
cams upon the hammers and a series of spirally disposed rollers formning a cam-way
upon the inside of the case which encases the entire machine, suitable devices being
also provided as set forth to rotate the tool in the intervals between the blows of
the hammers, and also to release and catch the hammers.
Second: The combination of parts substantially as shown and described
whereby the drill tool is rotated, with intervals of rest, the rotation occurring
between the blows of the hammors, and the teeth of the operating cam and genr
being kept out of contact while the blow is being delivered.
Third: The combination of parts substantially as shown and described for
producing the rotation of the hammer frame.
Fourth-The combination of parts substantially as shown and described for
giving the hammer blows, consisting of the hammers permitted to slide in grooves
in the revolving frame, and fed forward by spiral springs, the cains upon the
hammers and the roller cams upon the inside of the enclosing case, the whole
operating by means of the revolution of the hammer frame about its axis.
Fifth-The combination of parts substantially as herein set forth, whereby the
hammers are released to deliver their blow, and caught and held when forced back
against their driving springs, consisting as shown of a series of pawls and actuating
triggers.
Sixth-The combination of parts substantially as herein set forth, whereby the
tool is automatically fed forward, as the work progresses by means of a presser
foot connected to a clutch which throws the feed screw in and out of gear.
Seventh-The arrangement of parts, substantially as herein set forth, whereby
the automatic feed can be thrown out of gear and the feed mechanisin operated by
hand when required.
-
Eighth: The enclosing case covering the entire working mechanism and pro-
vided with the gates as shown, which, when opened, expose the entire mechanism
of the machine for examination and oiling.
Ninth The combination of parts substantially as herein set forth, whereby the
machine is supported upon a pillar in such a inanuer that it can be raised or
lowered bodily and adjusted to any angle vertical or horizontal.
Tenth The combination of parts, substantially as herein set forth, whereby
the machine can be rotated about an axis parallel but not co-incident with its own
axis, to permit of the removal and replaceinent of long drills without altering the
alignment of the work,

page_text: Eleventh-The peculiarly constructed and arranged cam-rollers set in the
enclosing case of the machine to operate the hammers.
Twelfth The loosely fitting helical spring, bearing at one end against a conical
internal support or thimble upon a stem of the reciprocating hammer and also at
the other end bearing upon a like thimble secured to the revolving hammer frame
opposite the end of the hammer, in combination with the said hammer frame and
hammer, substantially as set forth.