Improvements in Rock-drilling Machines.
Year: 1890

page_text: Date of Application, 16th Aug., 1890-Accented 27th Sept., 1890
COMPLETE SPECIFICATION.
[Communicated from abroad by URIAH CUMMINGS, of No. 375, Whitney Avenue,
New Haven, Connecticut, United States of America, Manufacturer.]
Improvements in Rock-drilling Machines.
I HENRY HARRIS LAKE, of the firm of Haseltine, Lake & Co. Patent Agents,
45 Sonthampton Buildings, in the County of Middlesex, 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 rock-drilling machines which are provided with
a reciprocating piston to the rod of which the drilling tool is attached.
The objects of my invention are to provide a simple valve-mechanism whereby the
point of cut-off can be changed so as to increase or reduce the length of the piston-
stroke also to provide a light and simple drill-supporting frame which can be
readily adjusted; also to provide a simple feed mechanism whereby the cylinder
of the drill-actuating piston is automatically fed forward, while it can be readily
returned; also to provide several other novel features of construction as will be
hereinafter set forth.
In the accompanying drawings,
Figure 1 is a longitudinal sectional elevation of my improved rock-drill.
Figure 2 is a plan view thereof.
Figure 3 is a cross section in line 11, Figure 1, on an enlarged scale.
Figure 4 is a horizontal section of the valve casing and valve mechanism in line 2, 2,
Figure 1, on an enlarged scale.
Figure 5 is a similar view of the valve-casing with the valve removed.
Figure 6 is a plan view of the valve detached.
Figure 7 is a horizontal section of the drill-feed mechanism and connecting parts
in line 3, 3, Figure 1.
Figure 8 is a transverse section in line 4, 4, Figures 1 and 7.
Figure 9 is a similar view in line 5, 5, Figure 1.
Figure 10 is a cross-section of the ratchet mechanism whereby the drill bar and
piston are rotated.
Figure 11 is a cross section in line 6, 6, Figure 1, on an enlarged scale.
Like letters of reference refer to like parts in the several figures.
A represents the longitudinally adjustable frame, which is mounted in a yoke or
saddle B, so that it can be adjusted toward and from the work. The adjustable
frame A is composed of two parallel side tubes or hollow bars a, a', secured with their
threaded ends in screw sockets a² formed on opposite sides of front and rear cross-
bars as a respectively, and two parallel intermediate guide rods or bars a³ a³ secured
with their ends to the cross bars a³ a between the side tubes a a¹.
The yoke B is provided with arched or outwardly and upwardly curved arms b,
which terminate at their upper ends in longitudinal sleeves 6 through which the
tubes a, a pass, and in which they are movably secured by clamping-rings 3, as
clearly represented in Figure 3. These clamping-rings are arranged in pockets or
openings formed in the sleeves midway of their length and opening downwardly.
These rings surround the tubes a, a' and are provided with upwardly projecting
screw-stems. The latter pass through openings formed in the sleeves, and are
provided with clamping-nuts or screw-threaded levers 65, whereby the rings 62, are
caused to tightly draw the tubes against the upper portions of the sleeves and
thereby secure the drill-frame against lengthwise displacement on the saddle. This
construction permits a considerable range of adjustment of the frame on the saddle
toward and from the work by simply loosening the clamping rings and shifting the
drill frame and without shifting the position of the tripod or supporting frame of the

page_text: machine, whereby a great saving of time is effected, especially when the drill is used
in tunnelling and similar work. The saddle B is provided at its lower central portion
with a circular,. or bevelled base whereby .it is secured to the tripod, column or
other support.
C represents the drill-cylinder arranged lengthwise between the tubes a a¹ and
movably supported upon the guide-rods as a by laterally-projecting lugs c, formed
on opposite sides of the lower front and rear portions of the cylinder C. The lags c
are divided longitudinally at their outer ends, where they are provided with set-
screws c whereby they can be closed upon the guide-rods as to take up wear.
D represents the piston arranged in the drill cylinder C and D the piston rod to
the front end of, which the drill bar or tool is attached in any well known manner.
The piston D of a front head d, a similar rear head d and an intermediate
reduced or connecting portion d². The space between the latter and the cylinder-
wall forms an annular inlet space or chamber e for the compressed air or other motive
fluid.
e represents the inlet-opening arranged in one side of the cylinder and com-
municating with the inlet-chamber e as represented in dotted lines in Figure 1 and
full lines in Figure 3.
represents the main compressed air supply pipe or hose, attached by a nipple e³
to the lower side of the socket a³ of the rear cross-bar a which communicates with
the side tube a¹ of the frame A, as represented in Figures 2, 7, and 8.
e represents a short flexible pipe or lose attached with one end to the tube a¹
in front of the saddle B and with its opposite end to the inlet opening el whereby
communication between the latter and the tube a¹ and main supply-pipe e² is
established.
By connecting the main supply-hose with the tube a' of the frame A and the tube a¹
with the cylinder by the hose e the cylinder is relieved of the weight of the main hose,
whereby friction and wear on the parts and the power required to move the cylinder
forward and backward is greatly reduced.
F represents the valve chamber arranged lengthwise of and above the drill-
cylinder and extending from end to end thereof.
Frepresents the rotary cylindrical valve, arranged snugly within the chamber F
and having its valve-stem which projects outwardly through a gland or stuffing box f
provided with a handle whereby the valve is turned or shifted.
gg represent radial induction-ports connecting the front and rear ends, respectively
of the cylinder with the front and rear ends of the valve-chamber F, and i
and represent similar intermediate inlet-ports which connect the central portion
of the cylinder with the valve chamber F. The inlet ports are adapted to
communicate with the rear portion of the cylinder through the valve and port gl
and the ports i and j with the front portion of the cylinder through the valve and the
front port g.
h represents a horizontal passage formed lengthwise on the front lower portion of
the valve F and connecting the inlet ports and j with the front induction port g.
represents a similar passage formed on the lower portion of the valve F in rear of
and in line with the passage h and connecting the inlet-port with the rear induction
port g¹. k represent similar passages formed in the valve F diametrically opposite
the passages. The passage is shorter than the passage and is adapted to
connect the front ports g and j and the passage is longer than the passage and is
adapted to connect the rear ports and g' when the valve is turned so that the
passages kk register with their ports.
L represents a longitudinal exhaust passage formed on one side of the valve
chamber F, and communicating at its front end with the valve chamber by the
transverse exhaust ports and m and at its rear end by similar ports m³ as
represented in Figures 4 and 5.
represents the main exhaust opening formed on one side of the exhaust passage
about midway of its length.
18
131³ represent vertical exhaust-passages connecting the forward end of the cylinder C

page_text: with the valve chamber F, and m² m² represent similar passages connecting the rear
end of the cylinder with the valve-chamber F.
nn represent curved exhaust passages formed on one side of the centre of the
valve F opposite the transverse exhaust-ports and vertical passages 1 m²
respectively and which are adapted to establish a communication between the vertical
exhaust-passages and m² and the transverse exhaust ports when the valve Fis
in the position shown in the drawings.
2 represent curved exhaust-passages formed on the opposite side of the valve F'
in advance of the passages n n' and opposite the transverse exhaust-passages m m¹ and
vertical exhaust passages 1 m³ and which are adapted to place the vertical passages 13 m³
in communication with their respective exhaust ports m m' when the valve F¹ is turned
or reversed.
As clearly shown in Figure 5 the front exhaust port m and vertical exhaust-
passage
13 are arranged in advance of the exhaust port and vertical exhaust passage l
in the forward end of the valve chamber and the exhaust port m' and vertical exhaust
passage mare arranged in advance of the exhaust port land vertical exhaust-
When the valve is in the
passage m in the rear portion of the valve chamber.
position represented in Figure 1, the exhaust passages and m² communicate with
the main exhaust passage L by means of the curved valve passages n n¹ as represented
in Figure 11 and the inlet chamber el can be placed in communication with the front
portion of the cylinder through the intermediate inlet-ports ij passage and front
induction port g and with the rear portion of the cylinder through the intermediate
inlet-port passage h¹ and rear induction port g'. When the piston is at the limit of
its forward movement ready to begin its return stroke as shown in Figure 1 the rear
exhaust port m² is open, the inlet-port is closed by the rear head d' of the piston the
inlet ports i and j leading to the front end of the cylinder are open and the front
exhaust passage is closed by the front head d of the piston. Compressed air will
now pass from the inlet chamber e to the front portion of the cylinder through the
inlet ports ij passage h and front induction port g and cause the piston to move
backwardly. During the backward movement of the piston the intermediate inlet
ports ij are closed by the front head d of the piston, and as soon as these ports have
been closed the exhaust passage 12 is opened and at the same time that the latter is
opening the inlet port leading to the rear portion of the cylinder, is also opened by
the front portion of the rear head d of the piston, so as to allow compressed air to
enter back of the piston. The latter continues its backward movement by the
momentum until the backward movement is arrested by cushioning against the
increasing compressed air. When the piston is at the limit of its backward movement
as indicated in dotted lines in Figure 1 the rear exhaust passage m² is closed the
intermediate inlet passage i¹ leading to the rear portion of the cylinder is open the
intermediate inlet-ports ij leading to the front portion of the cylinder are closed and
the front exhaust port is open. The compressed air back of the piston will now
cause the latter to move forwardly. During this forward movement the intermediate
inlet port is closed by the rear head of the piston and as soon as this port is
closed the rear exhaust passage m² is opened and at the same time that the latter is
opening the inlet-port i leading to the front portion of the cylinder, is also opened by
the front head d of the piston so as to allow compressed air to pass to the front
portion of the cylinder in front of the piston. The forward movement of the piston
continues until it is arrested by cushioning against the incoming compressed air when
it is ready for the return stroke.
When it is desired to shorten the stroke of the piston so as to increase its speed and
cause the drill to render quicker blows as in starting a hole the valve F¹ is turned by
the handle until the passages ¹ register with the inlet ports g j and jig
respectively. This adjustment of the valve F' causes the exhaust passages and m²
to be closed and the exhaust passages and m³ to be placed in communication with
the respective exhaust ports mm² and the exhaust passago L by the valve-passages n² n³
respectively and the front inlet port i to be closed and the rear inlet port it to remain
open. In this position of the valve compressed air is admitted to the front portion of

page_text: the cylinder through the front inlet port passage k and front induction port g and to
the rear portion of the cylinder through the rear inlet-ports passage and rear
induction port g. When the piston is in the position indicated in Figure 1, ready to
begin its backward movement, the inlet port j is open the front exhaust port
is
closed the rear inlet ports and are closed and the rear exhaust port m³ is open.
It will now be apparent that the piston D will move backwardly only one half the
distance before its front head will close the front inlet-port and open the front
exhaust-port 3, and its rear head d' open the rear inlet-ports and close the rear
exhaust-port m³, whereby the piston will be reversed at about one-half of its former
stroke both forwardly and backwardly. The valve F is allowed to remain in this
position until the drilling-tool has entered the hole sufficiently to be guided therein,
when the valve is shifted so as to cause the piston to make full strokes.
In my improved valve-construction the valve is stationary and the compressed air
or other actating fluid is quickly directed to one side of the piston or the other
without requiring the moving or shifting of the valve for this purpose, whereby the
piston speed is greatly increased. The points of cut-off and exhaust are shifted by
simply turning or reversing the valve, which is an extremely simple operation and
renders this mechanism very convenient in use.
P represents a spirally-grooved rod journaled in the rear head of the cylinder C
and engaging with its front end in a spiral socket in the rear head d' of the piston.
» represents a ratchet-wheel secured to the outer end of the spiral rod P and
arranged in a cap or casing pl secured to the outer side of the rear cylinder-head.
P represents pawls, whereby the ratchet-wheel is held against retrograde movement.
This mechanism serves to rotate the piston and drill at each backward stroke in a well
known manner.
represents the feed-cylinder arranged longitudinally underneath the drill-
cylinder C, and secured at its front ond in a threaded lng g formed on the lower front
portion of the cylinder C and supported about midway of its length in a loop g'
formed on the lower rear portion of the cylinder C.
R represents a stationary piston fitted snugly in the feed-cylinder Q, and R' the
piston-rod passing through a gland and secured with its rear end to the central
lower portion of the rear cross-bar a' by a screw nut ¹.
72 is a screw-cap closing the front end of the cylinder Q.
S
represent longitudinal passages formed in the piston rod R and communicating
on opposite sides of the rear portion of the piston-rod R¹ with the transverse
passages ss provided with stop-cocks S S¹. The latter are provided at their upper
ends with handles 3 whereby they can be turned. The passages passes through the
piston and opens into the cylinder in front of the piston, and the passage s¹ terminates
immediately in rear of the piston R and opens into the cylinder in rear of the
piston.
As represented in Figures 1 and 8 t represents a transverse feed-passage formed in
the lower portion of the cross-bar a and opening into the socket a² connected with
the main air-supply pipe e and represent longitudinal passages connecting the
outer ends of the transverse passages 23 respectively with vertical ports ³ ³ leading
to the transverse feed-passage t.
represents the transverse inlet-passages of the stop-cocks S S₁ and 16 curved
outlet or exhaust passages formed on one side of the stop cocks SS' and which are
adapted to connect the inner portions of the passages 23 with exhaust openings t
formed in the casings of the cocks and leading to the outer air.
When the drill cylinder is in its rearward position on the frame A, as shown in
Figures 1 and 7 and it is desired to feed the same forwardly the stop-cock S is turned
so as to place its inlet passage t into register with the transverse passage s² and
admit the compressed air from the latter through the longitudinal passages to the
space of the feed cylinder Qin front of the piston R. The stop cock S¹ is then turned
so that its exhaust passage to registers with the transverse passages and exhaust
opening whereby the space in the feed cylinder in rear of the piston is placed in
conmunication with the outer air through the longitudinal passage s¹ transverse

page_text: passage cock-exhaust passage to and the exhaust passage t7. The compressed air
in front of the piston now causes the feed-cylinder to move forwardly so as to feed
the drill-cylinder C and the drill. The speed of this forward movement of the
cylinder is readily regulated by simply turning the stop-cock S¹ so as to increase
or diminish the size of the exhaust orifice and control the escape of the air from the
cylinder in rear of the piston. When it is desired to return the cylinder Q to its
normal position after the feed-cylinder has been moved to the limit of its forward
movement or at any other point the cock S is turned so as to allow the air in front of
the piston to exhaust through the cock passage and exhaust opening and the
cock S¹ is turned to admit the compressed air to the space in rear of the piston, thereby
moving the feed cylinder and drill cylinder backward to the point of beginning.
This backward movement of the cylinders is much more rapid than when a feed-screw
is employed whereby a great saving of time and labor is effected.
I prefer to employ compressed air as the motive power but it is obvious that in its
stead any other suitable fluid under pressure may be used.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed as communicated to me by
my foreign correspondent, I declare that what I claim is :-
:-
First. The combination with a valve-chamber provided. with different ports of an
adjustable stationary valve arranged in said chamber and provided with corresponding
ports whereby different ports in the valve chamber can be called into action at desire
by adjusting the valve, substantially as set forth.
Second. The combination with a valve chamber provided with end ports and with
a plurality of intermediate ports for each end port of an adjustable stationary valve
provided with longitudinal ports of different length whereby either of the intermediate
ports can be placed in communication with the corresponding end-port by adjusting
the valve, substantially as set forth.
Third. The combination with the cylinder provided with a central inlet for the
actuating fluid and with end ports and intermediate ports of a piston provided with a
central cavity for the reception of said fluid and an adjustable stationary valve
provided with different ports whereby the stroke of the piston can be changed by
adjusting the valve substantially as set forth.
Fourth. The combination with the supporting yoke or saddle of a longitudinal drill
frame provided with parallel side bars, which are adjustably secured to the yoke or
saddle and with intermediate guide-bars arranged parallel with the side bars and a
drill cylinder movably supported on the intermediate guide bars, substantially as
set forth.
Fifto. The combination with the supporting yoke or saddle of a longitudinal drill-
frame provided with parallel side bars which are adjustably secured to the yoke or
saddle and with intermediate guide bars arranged parallel with the side bars, a drill
cylinder movably supported on said intermediate guide-bars and feed mechanism
connected with the drill cylinder whereby the latter is moved on the guide bars,
substantially as set forth.
Sixth. The combination with the supporting yoke provided with longitudinal fixed
sleeves, of a drill frame having its side bars arranged adjustably in said sleeves and
clamping sleeves arranged in said fixed sleeves and embracing the side bars of the
drill-frame whereby the latter is secured in place, substantially as set forth.
Seventh. The combination with the supporting yoke provided with longitudinal
fixed sleeves having pockets opening through the walls of said sleeves of a drill frame
having its side bars arranged adjustably in said sleeves and clamping sleeves embracing
the side bars of the drill frame in said pockets and provided with screw-shanks and
nuts whereby the side bars of the frame are tightened against the sleeves of the yoke
substantially as set forth.
Eighth. The combination with the drill cylinder of a hollow supporting frame a
flexible pipe or hose connecting the hollow frame with the drill cylinder and a supply

page_text: pipe or hose connected with the hollow frame whereby the drill cylinder is relieved
from the weight of the supply pipe, substantially as set forth.
Ninth. The combination with the drill-cylinder and piston and its supporting frame
of a feed cylinder and piston whereby the drill cylinder is moved on the supporting
frame substantially as set forth.
Tenth. The combination with the drill-cylinder and piston and its supporting frame,
of a feed piston secured to said frame and a feed-cylinder secured to the drill-cylinder
substantially as set forth.
Eleventh. The combination with the drill-cylinder and piston and its supporting
frame of a feed-cylinder secured to the drill cylinder and a feed piston and rod
secured to the frame and provided with longitudinal passages for the actuating fluid
opening into the feed cylinder on opposite sides of the piston substantially as set
forth.
Twelfth. The combination with the supporting frame of a drill cylinder movably
mounted on said frame a feed-cylinder attached to the drill-cylinder a piston and rod
arranged in said feed-cylinder and attached to the frame fluid passages formed in said
piston and rod and cocks arranged in said fluid passages whereby the fluid pressure
can be admitted to or exhausted from either side of the feed piston, substantially as
set forth.
Thirteenth. The combination with the drill-cylinder and its hollow supporting
frame connected with a pipe through which the actuating fluid enters the hollow frame
of a feed cylinder attached to the drill-cylinder a piston and rod secured to the hollow
frame and arranged in the feed cylinder longitudinal fluid-passages formed in said rod
and opening into the feed cylinder on opposite sides of the piston a transverse passage
formed in the frame and communicating with the fluid cavity of the frame, branch
passages connecting said transverse passage with the longitudinal passages in the
piston rod and cocks arranged in said branch passages whereby the fluid pressure
can be admitted to or exhausted from either side of the feed piston, substantially as
set forth.
Dated this 16th day of August 1890.
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C., Agents for the Applicant.