An Improved Fluid-pressure Engine for Blowing Organs.
Year: 1893

page_text: Date of Application, 28th Feb., 1893
Complete Specification Left. 28th Nov., 1893-Accepted, 30th Dec., 1893.
PROVISIONAL SPECIFICATION.
An Improved Fluid-pressure Engine for Blowing Organs.
We HENRY WILLIS and VINCENT WILLIS, both of Rochester Terrace,
Camden Town in the County of Middlesex, Organ Builders, do hereby declare
the nature of this invention to be as follows
-
The object of the present invention is to provide an engine for operating the
feeders of an organ bellows in their usual horizontal position under the reservoir
(without the intervention of mechanism), noiselessly, and in such a manner as will
produce a continuous blast of compressed air.
By the present invention an even regular and ample supply of compressed air
may be secured by four or more, or even a less number of feeders, but as bellows
should be rectangular, a square being the most economic form for them, 4 square
feeders under a square reservoir is theoretically and practically the best arrange-
ment, and it will therefore be taken as a most favorable example in explaining the
nature of the present invention.
Under each of the four feeders, there is established a single acting cylinder,
or ram, capable of lifting the feeder the required distance. The feeder and ram
may be rigidly connected. Centrally and vertically between the cylinders is fixed
a valve box containing a circular rotating valve. Four supply ports are arranged
in the valve seat, and connected to the cylinders by pipes. Discharge ports, com-
municating with a discharge chamber below, are also provided in the seat, preferably
in a circle within, and concentric with, that formed by the supply ports. The
circular rotating valve is perforated with a ring of supply ports corresponding
The number of the
in diameter with the ring of supply ports in the valve seat.
supply ports will differ, say, four for the valve seat, and three for the valve, and
they are so arranged that a part of one of the ports in the valve seat will always
be uncovered.
The valve is channelled on its under face for three discharge ports leading to
the discharge ports of the valve seat. A central perforation, preferably square, is
made in the valve, to receive the valve spindle, on which it is loosely fitted. The
valve spindle extends below the valve into a socket bearing, and upwards through
a stuffing box or gland. On the upper end of the valve spindle, beyond the
valve box, is fixed a pawl wheel having two ring grooves in its periphery. Near
the bottom of the grooves, are three pins, situate, in this case, 120 degrees apart.
The grooves act as guides to four travelling horizontal pawls, which, through bell
cranked levers or their equivalent, are actuated by the rams connected with the
feeders. These pawls are arranged to engage the pius in the grooves of the
pawl wheel, and thereby to drive the valve spindle at the right instant,
the amount of travel allowed to the pawl being sufficient to rotate the circular
valve about 30 degrees, with a proper excess to ensure certain reengagements.
The action of the apparatus is as follows:-
Water or compressed air being admitted to the valve box (above the valve),
finds one supply port partly open, and passing down to the cylinder in communi-
cation therewith, forces its ram and feeder upwards, at the same time causing the
travelling pawl connected with the rising ram to move and engage the pin of
the pawl wheel on the valve spindle. By this means, the valve will be rotated
until the open port is nearly closed. But before the port is quite covered, another
will be opened, which, admitting water to the next ram, will cause it to rotate the
valve in a similar manner, and thus will be produced, by intermittent strokes of the
pawls, a practically continuous rotation of the valve. The weight of the feeders
and rams serves to expel the water or other motor through the discharge ports into

page_text: the discharge chamber, and at a speed determinable either by the area of the ports
or the area of the inlet valves of the feeders.
To prevent noise, the rams may be allowed to fall on buffer springs in their
cylinders, or the inlet valves of the feeders may be controlled.
It is preferred to make the perforated supply ports of the rotating valve smaller
than the ports of the valve seat leading to the cylinders, in order to obtain a
quicker return stroke. The travelling pawls may be curved in such a manner as
to act noiselessly.
The speed of the rotating valve varies exactly with the opening and closing
of the supply ports, and if the pawl clearance is not excessive, the valve is
always moving, admitting water to each ram in succession, without the slightest,
shock.
It is obvious that 2, 3, 4, or more rams may operate feeders on this system, and
that it is also applicable to 2 or more double-acting cylinders, if the rotating valve
and its seat are suitably ported, the essential principle being that each pawl, before
quite completing the closing of a port, shall open another port, and thus produce
a continuous action.
Dated this 28th day of February 1893.
NEWTON & SON,
Agents for the Applicants.
COMPLETE SPECIFICATION.
An Improved Fluid-pressure Engine for Blowing Organs.
We HENRY WILLIS and VINCENT WILLIS both of Rochester Terrace,
Camden Town in the County of Middlesex, Organ Builders, 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 :-
The object of the present invention is to provide an engine for operating the
feeders of an organ hellows situate in their usual horizontal position under the
reservoir (without the intervention of mechanism), noiselessly, and in such a manner
as will produce a continuous blast of compressed air.
By the present invention, an even, regular, and ample supply of compressed air
may be secured by four or more, or even a less number of feeders, but as bellows
should be rectangular, a square being the most economic form for them, 4 square
feeders under a square reservoir is theoretically and practically the best
arrangement.
For the purpose of avoiding complexity in the drawings, we have thought it
desirable to illustrate our invention and describe its characteristics first as arranged
for working a pair of feeders which are each actuated by a ram controlled by a
single rotary valve common to both, and secondly to explain the manner of
carrying out the invention in its most approved form.
In the accompanying drawings,
Fig. 1 shows in plan view our improved fluid-pressure engine adapted to work a
pair of feeders.
Fig. 2 is a sectional elevation shewing one feeder with its cylinder, ram, valve
chest, and connections. It may be here remarked that one valve and one valve-
chest, suitably ported, may be employed to operate any given number of rams.
The cylinder shown is therefore common to any arrangement of vertically-acting
feeders.
In these figures, A A* are the hydraulic cylinders, and B B* are rams
permanently connected with their respective feeders C (Fig. 2), for the purpose of
actuating the same for inflation of the bellows.
The feeders actuated by their respective rams transmit rotary motion
alternately, by means to be presently described, to a rotary valve D, which
works on the horizontal seat of a valve chest E. This valve is carried by a

page_text: squared vertical spindle F, upon which is also mounted a pawl wheel G, that
receives from the feeders an intermittent axial motion which it imparts through the
spindle F to the valve D.
It is through this valve and its valve chest that the water or fluid motor under
pressure employed for working the organ bellows is admitted to and discharged
from the cylinder A.
The ram B, it will be seen, is rigidly connected with the feeder C (situate
immediately above it) by a rod and thrust block.
The cylinder A has a perforated diaphragm or false bottom A', which forms a
seat for a flanged valve b, loosely fitted to, and carried by the ram.
From the bottom of the ram depends a short stem 6' to receive this valve b, which
below its flange has a tapering extension downwards to enter and gradually close
the opening in the diaphragm or bottom of the cylinder.
The stem has a head at its extremity, through which is drilled vertically
a series of holes, and extending upwards from these holes are vertical channels or
flutes cut in the periphery of the stem, which channels diminish in size, and vanish
near the top of the stem.
The object of the valve 6 and its seat A¹ is to provide a water cushion for the
ram on its return stroke, the efficiency of which cushion can be determined to nicety
by varying the size and length of the boles and channels. The ram at its in or
return stroke first restricts the overflow of water by lowering the tapering extension
of the valve into the aperture in the valve seat, and, after scating the valve,
further gradually restricts the outflow by the varying depth or capacity of the
channels in the stem. The ram, in completing its travel by sliding its stem 6' in
the now arrested valve, gradually covers the vanishing channels, and cuts off all
but the leakage between the valve and stem, and comes to rest noiselessly.
Where a high speed is required, the valve may be perforated with some small
holes which must be covered by a thin disc valve also strung on the guide stem.
This treatment permits of a quicker start being made without interfering with the
water cushion, but it is not required for ordinary speeds.
We will now describe the connection of the feeder with the pawl wheel G which
gives the intermittent axial motion to the controlling valve D.
Pivotted to the thrust block fitted to the feeder C, is a pair of pendent rods the
lower ends of which are pivotted to arms / keyed to a rock shaft H, which shaft
has its bearings in brackets cast on the cylinder A.
Keyed to, and standing up from the rock shaft, is an arm A, and to & pin
adjustable in a slot of this arm is attached, by means of a ball and socket joint, a
pawl rod g designed to actuate the pawl wheel G.
The arrangement just described is duplicated, as will be seen with reference
to Fig. 1, and the pawl rod 9*, actuated by the ram B* working alternately with
the pawl rod 9 on the pawl wheel G, causes the intermittent rotation of that
wheel.
The periphery of the wheel G has two annular grooves to receive respectively
the pawl rods g and g*.
In each of these grooves are fitted four pins, set equidistant from each other,
and serving as teeth for the pawls respectively to act upon during their back
motion.
The pins of one groove are set intermediate of those of the other groove, so as to
equalise the intermittent action of the two pawl rods, and complete the rotation of
the pawl wheel by eight equal movements.
The pawl wheel thus actuated imparts a corresponding rotary motion to the
valve D, and thereby admits water under pressure to the cylinders A A*, and opens
discharge ports for the escape of the same.
To understand the action of the apparatus for the production of a continuous and
equable supply of air to the reservoir, it, is important to observe not merely the
construction, but the relative positions of the ports in the valve and valve chest.
Fig. 3 shows in plan view the seat of the valve chest E, the ports of which are

page_text: equi-distant from each other, the supply ports forming an outer ring of holes, and
the discharge ports an inner ring of holes. These latter pass down through the
solid portion of the valve chest E, and end in a chamber e, which is in communication
.with the exhaust pipe e¹.
Figs. 4 and 5 show in plan views the opposite faces of the rotary valve D, Fig. 4
shewing the supply ports, and Fig. 5 the channels or recesses which connect the
inlet ports of the valve chest with the exit ports thereof.
From the foregoing description it will be understood that the valve D is arranged
to operate two feeders. This we prefer to do by using only one supply and one
discharge port, dividing each into 4 smaller ports, in order to reduce the angular
advance for effecting, by means of eight impulses, one complete rotation of the
valve. The ports leading respectively to the cylinders A A* are united by the
circular cored-out chambers of the valve chest, as shown in the sectional
view, Fig. 2. This arrangement avoids idle valve seat surface, and gives the
greatest efficiency for a given diameter of valve.
It is necessary that the ram in action shall start its successor. This is effected
by so arranging the supply ports of the valve with respect to the supply ports in
the valve chest, that while the leading port is opening, the following port shall be
closing, as best illustrated at Fig. 14, which is an enlarged sectional plan of the
valve chest with the valve in place. In this figure the valve ports are represented
by drawn lines and the valve chest ports by dotted lines. The supply ports are
thus virtually extended, so as to open in advance a portion of the ports in the
valve chest leading to both rams.
Both rams are therefore receiving water at the same time, one in diminishing
quantity, and the other in increasing quantity. As both rams thus travel together
on the out-stroke for a short distance, a quick instroke becomes necessary.
This is
naturally accomplished by spacing the discharge ports equally, so that all open
simultaneously, and not in succession, as is the case with the supply ports.
According to the drawing, the supply ports close in succession. This is not
essential, as they might be arranged to close simultaneously like the discharge
ports; they would then be of unequal length.
It is obvious that the maximum speed of this engine is determined by the rate
at which the feeders and rams fall under the action of gravity; the discharge
ports should therefore be large.
At starting, and before the full load is on the feeders, there is a risk of over-
running the maximum speed. This can be prevented by interposing a thin
perforated diaphragm (adjusted to each engine) at the inlet to the valve chest.
.
An engine applied to an organ is frequently at rest for long periods, and may
be stopped from the locality of the key-boards, regardless of position. A ram
arrested at the extremity of its outstroke would remain so, for the rotary valve
becomes perfectly sound, or watertight, and it is possible that the U leather might
adhere to the ram, and prevent it falling when the engine is again required for use.
This can be prevented by arranging an extra pawl rod to be operated by the
bellows in subsiding, which shall turn the valve just sufficient to release the ram
that may be in the acting position.
Fig. shows in partial plan view, and Fig. 7 in partial vertical section, an
arrangement of our invention for actuating four feeders.
Fig. 8 is a plan view of the valve seat modified to suit this arrangement, and
Fig. 9 is a top view of the valve, furnished with three supply ports in place of four,
as shown at Fig. 4.
It will be understood that in this arrangement there is established, under each
of the four feeders, a single acting cylinder or ram capable of lifting the feeders the
required distance. The feeder and ram are, as before explained, in direct connection.
Centrally and vertically between the group of four cylinders, the valve chest E is
fixed, containing the circular rotating valve D. Four supply ports are arranged
in the valve seat, and connected to the cylinders by pipes a a¹ a² a³. A corre-
sponding number of discharge ports communicating with the discharge chamber e

page_text: are also provided in the chest, in a circle within, and concentric with, that formed
by the supply ports. The circular rotating valve is perforated with a ring of three
supply ports equidistant from each other, corresponding in diameter with the ring
of supply ports in the valve seat. By this arrangement of the ports, a part of
one of the ports in the valve seat will always be uncovered.
The valve is channelled on its under face, for connecting the supply ports in the
valve seat with the discharge ports. The valve is mounted, as already described,
on a spindle which carries, at its upper end, a pawl wheel G, having two ring
grooves in its periphery. Near the bottom of the grooves are three pins, situate,
in this case, 120 degrees apart. The grooves act as guides to four travelling
horizontal pawl rods g g' 93 9³, which, through bell-crank levers or their equivalent,
as already explained, are actuated by the rams connected with the feeders. These
pawls are arranged to engage, in succession, the pins in the grooves of the pawl
wheel, and thereby to drive the valve spindle intermittently, the amount of travel
allowed to each pawl being sufficient to rotate the circular valve about 30 degrees,
with a proper excess to ensure certain re-engagement.
The action of the apparatus is as follows:
--
Water or compressed air being admitted to the valve chest (above the valve),
finds one supply port partly open, and passing down to the cylinder in communica-
tion therewith, forces its ram and feeder upwards, at the same time causing the
travelling pawl connected with the rising ram to move and engage the pin of the
pawl wheel on the valve spindle. By this means the valve will be rotated until
the open port is nearly closed. But before the port is quite covered, another will
be opened, which, admitting water to the next ram, will cause it to rotate the valve
in a similar manner, and thus will be produced, by intermittent strokes of the
pawls, a practically continuous rotation of the valve. The weight of the feeders
and rams serves to expel the water or other motor through the discharge ports
into the discharge chamber e, and at a speed determinable either by the area of the
ports, or the area of the inlet valves of the feeders.
To prevent noise due to the falling of the rams, we employ the device described
with reference to Fig. 2 in each cylinder. -
It is obvious that 2, 3, 4, or more rams may operate feeders on this system, and
that it is also applicable to 2 or more double-acting cylinders, if the rotating valve
and its seat are suitably ported, the essential principle being that each pawl,
before quite completing the closing of a port, shall open another port, and thus
produce a continuous action.
In Fig. 10 we have shown the adaptation of our improved rotating valve gear
to the usual arrangement of double acting engine and feeders.
It will be understood that to produce a smooth and ample supply of air to the
reservoir, this apparatus must be duplicated, the action of the two apparatuses being
controlled by the one rotating valve and valve chest, as heretofore explained. In
this figure, the same letters of reference are used as in the corresponding parts of
the before described figures.
Having now particularly described and ascertained the nature of the said inven-
tion and in what manner the same is to be performed, we declare that what we
claim is :-
1. Controlling the movement of hydraulic rams or pistons applied to the feeders
of organs, by means of a suitably ported intermittently rotating valve working in
connection with a valve chest, as described, and actuated either from the feeders of
the organ or the rams or pistons of the engines.
2. The arrangement of the ports and channels in the valve and valve chest of
the hydraulic engine, as described with reference to Figs. 14, 2, 3, 4, 5, 7, 8 and 9
of the accompanying drawings.
3. The means above. described for transmitting motion from the feeders to the
controlling valve, so as to secure a continuous action of the motor engines.

page_text: 4. Cushioning the ram in its return motion in the manner and for the purpose
above set forth.
5. Arranging single-acting pressure engines immediately below their respective
feeders, as above described, for the purpose of supplying an uniform and continuous
blast of air to organ reservoirs.
Doted this 27th day of November 1893
NEWTON & SON,
Agents for the Applicants.