Improvements in Steam Engines.
Year: 1898

page_text: Date of Application, 30th Aug., 1898-Accepted, 3rd Dec., 1898
[Communicated from abroad by CHARLES CAMPBELL WORTHINGTON, Mechanical
Engineer, of Irvington, in the County of Westchester, and State of New
York, United States of America.]
Improvements in Steam Engines.
I, HENRY EDWARD NEWTON, of the Office for Patents, 6, Bream's Buildings,
Chancery Lane, in the County of London, Patent Agent, do hereby declare the
nature of this invention and in what manner the same is to be performed, to be
particularly described and ascertained in and by the following statement:-
-
This invention relates to steam and similar expansion engines, in which the
admission of the steam or other motor fluid is cut off before the piston stroke is
completed, and more especially to that well-known class of such direct-acting
engines which are provided with one or more compensating or auxiliary cylinders
and pistons, which are supplied with a suitable motor fluid, and are arranged to
act in opposition to the main piston or pistons during the first part of the stroke
of the latter, and in conjunction therewith during the last part of the stroke, so
that the admission of steam to the main cylinder or cylinders may be cut off
before the stroke is completed, without reducing the power of the engine at the
end of the stroke.
One part of the invention relates to an improved valve movement for thus
cutting off the steam before the stroke is completed, the improved valve move-
ment being of that class in which a single valve controls both the admission and
cut-off of the steam or other motor fluid. The improved valve movement is ap-
plicable generally in steam and similar expansion engines, both single and
multiple cylinder, but it is especially adapted for use with duplex direct-acting
steam pumps and similar duplex engines, and the particular object of this part
of the invention is to provide an improved movement for such engines, by which
the opening of the valves for the admission of steam or other motor fluid is con-
trolled by the opposite side of the engine, and the closing of the valves for cutting
off the steam or other motor fluid is controlled by their own side of the engine.
Another part of the present invention relates particularly to pumping engines
employing a compensating cylinder or cylinders connected to the force main, so
that the compensating cylinder pressure is dependent on the force pressure. The
chief object of this part of the invention is to provide a simple and efficient con-
struction by which the desired action of the compensating cylinders shall be
secured under sudden or wide differences of pressure in the force main, the pro-
duction of pulsations in the column of fluid in the force main by action of the
compensating cylinders be avoided, and a smooth and efficient operation of the
apparatus, under all running conditions, be secured. The broader features of
this part of the invention are applicable in connection with engines of any form
employing one or more compensating cylinders, but the invention includes also
certain combinations in duplex engines, in which engines the relative movement
of the pistons on each side, and the control of each side by the other through the
valve movement and connections for supplying fluid to the compensating cylin-

page_text: ders, results in a special action of the compensating apparatus, not existing in
single engines, and it includes also certain features that are not limited to con-
structions in which the compensating pressure is derived from, or dependent on,
the force pressure.
While this part of the invention relates especially to compensating steam en-
gines, it also includes certain features of construction that may be used in other
apparatus, one of the specific objects of this part of the invention being to provide
an efficient means by which pulsations or variations in the pressure of the force
main of pumping engines may be relieved through the medium of air pressure,
without requiring the air pressure to be the same or as great as that of the main
pressure, so as to secure the well known advantages of the ordinary air chamber,
without the necessity of maintaining the air pressure at a point which would be
difficult, in the case of pumping engines working under unusually high pressure
in the force main.
"
The various improvements constituting the present invention will now be
described in connection with the accompanying drawings, in which a pumping
apparatus is shown embodying all the features of the invention applied in their
preferred form in connection with a Worthington" compound duplex direct-
acting pumping engine, and a modified construction embodying some of the
features of the invention, and the various parts of the invention will be then
specifically pointed out in the claims.
In the drawings,
Figure is a side elevation of the pumping apparatus ;
Figure 2 is a plan view of the same;
Figure 3 is a detail sectional elevation, on an enlarged scale, of the connections
between the force main and the compensating cylinders.
Figure 4 shows a Worthington triple expansion duplex direct-acting pumping
engine, with my improved valve movement, and an accumulator between the air
chamber of the pump and the compensating cylinders.
Figures 5 and 5ª are diagrammatic sectional views of the high-pressure cylin-
ders on opposite sides of the engine, looking in the same direction as Figures 1
and 4, and showing the parts of the valve movement in the same position as in
the general views.
Figures 6 and 6^ are similar views of the valve movement, showing the parts in
another position.
Referring to the said drawings, the engine shown is, in general construction,
a "Worthington" horizontal compound direct-acting duplex-pressure pumping
engine, having the high and low pressure cylinders A, B and A, B on opposite
sides arranged in line, and two water cylinders C, C on opposite sides of the
pump, and having suction main D and force main E connected with the cylin-
ders C, C through valve pots on top of the water cylinders, as well known in
connection with such pressure pumps. The plungers F, F¹ are shown as extend-
ing through the water cylinders, and connected by side rods f, fl to cross-
heads 9, g', on opposite sides of the engine, which are connected to the high pres-
sure pistons on opposite sides by the main piston rods Y, Y, and the low pressure
pistons are connected to these cross-heads by side rods y, y¹ on opposite sides of
the high pressure cylinders. To these cross-heads are connected also the pistons
of the compensating cylinders G G¹, on opposite sides of the engine, two com-
pensating cylinders being shown, although it will be understood that a single
cylinder, or more than two cylinders, on each side, may be used, these compen-
sating cylinders receiving fluid through their hollow trunnions, as usual in such
constructions, from cross pipes H connecting the trunnions of the upper and
lower pairs of cylinders on opposite sides, and a pipe I connecting the accumu-
lator with these cross pipes. Steam is supplied to the high pressure cylinders
through the induction pipe Z, the exhaust passing from the high pressure to the
low pressure cylinders through the pipe 7, and the low pressure cylinders
exhausting through the pipe Z to the condenser, or otherwise, as desired.

page_text: Referring now to the steam valve movement by which the admission of steam
is cut off before the pistons reach the end of their strokes, the steam cylinders are
constructed with the admission ports 1 at the top of the cylinders, and separate
exhaust ports 2 at the bottom of the cylinders, the admission and cut-off on oppo-
site sides of the engine being controlled by oscillating valves a, a, a single valve
at each end of each cylinder, and the exhaust ports 2 by similar oscillating
valves b, b. The admission and cut off valves a, a' are each connected by crank
arms 12 on the valve stems and links 13 to rockers c, c', the connection between
the rockers and links being made through the connection blocks 3, adjustable
so as to secure the cut-off at the desired point, and these rockers c, el are pivotally
mounted, by suitable pivots 4, on moveable members, which, in the preferred
form shown, have an oscillating movement, and consist of the rockers, d, don
the steam cylinders, these rockers d, d, also actuating the separate exhaust
valves b, 6, through crank arms 14 on the valve stems, and links 15 connecting
the crank arms with the rockers d, .
.
The rockers c, c¹ of the low-pressure cylinders are connected to the rockers c, c¹
of the high-pressure cylinders by connecting rods 16, pivotally connected to the
rockers by pivots 5, so as to be actuated together, and the rockers c, c¹ of the high
pressure cylinders are pivotally connected by pivots 5 to connecting rods 17, the
other ends of which are connected to swinging levers e, e¹ on the opposite sides
of the engine, which are connected to the piston-rod heads on the same side of
the engine by links 18. Each of the rockers c, c', therefore, has two pivots,
pivot 4 on the rocker d or d¹, and pivot 5 to the direct-actuating connections of
the rocker, and the rockers c, e are oscillated upon these pivots respectively for
cut-off and admission.
The rockers d, d of the low-pressure cylinders are connected to the rockers d, d'
of the high-pressure cylinders by connecting rods 19, so as to be actuated there-
with, and these rockers are connected by connecting rods 20 to crank arms 21 on
cross-over rock shafts S, T, which are actuated by the piston rods through the
valve movement levers N N' and links 22 from the cross-heads on the opposite
sides of the engine, the rock shaft S thus being actuated from the A cylinder
side of the engine, and the shaft T from the A cylinder side of the engine, each
of the rockers d, d' thus being actuated from the opposite side, of the engine for
admission and exhaust. It will be understood, however, that the exhaust valves
may be actuated by any other suitable connections to the opposite side of the
engine, instead of through the rockers d, d', although the construction shown is
preferred.
The operation of this valve construction will be understood from the drawings,
with a brief description referring especially to Figs. 5 and 5 and 6 and 6.
As shown in Figures 5 and 5, piston X is just about to start on its stroke to
the left, the valve, a, at the right end of the cylinder A having been opened by
the movement of the piston X on the opposite side of the engine, which is now
moving to the left, and is somewhat past the middle of its stroke. As the pis-
ton Xmoves to the left, its piston rod, by the link 18, connected to the crosshead,
moves the lever, e, in the same direction as the piston, that is, to the left, in
Figure 5, and thus, through the link 17, swings the rocker c to the left upon its
pivot 4, and thus, through the link 13 and crank-arm 12, actuates the valve a at
the right end of the cylinder A, so as to close this valve, and cut off the steam
at the proper point, which is about one-third stroke in the construction shewn.
This movement of the rocker c moves the valve a, at the left end of the cylin-
der A slightly, but on account of the relation of the arc of movement of the left
arm of the rocker c and link 13 to the crank arm 12 on this valve, the movement
is not sufficient to open the valve, as it is obvious from the drawings that the
end of the link 13 connecting this valve to the rocker, moves nearly in the arc
of a circle about its pivot to the crank arm 12. Meanwhile the piston X¹ has
continued its stroke to the left, and is just about to finish its stroke, after which
it will be reversed by the opening of the admission valve a¹, at the left end of

page_text: .
the cylinder A' and the shifting of the exhaust valves b', so as to close the ex-
haust valve at the left end of the cylinder A', and open that at the right end of
this cylinder, which is secured by the movement of the piston X of cylinder A,
as hereinafter described. The valve and valve movement parts of the high pres-
sure cylinders on the opposite sides of the engine are now in the position shown in
Figures 6 and 6. As the parts continue their movement from the position shown in
Figures 6 and 6, the piston X, through the link 22, connected to its cross-head
and lever N, rocks the shaft S to the left, in Figure 6, and thus through crank
arm 21 on the A' cylinder end of its shaft and link 20, moves the lower side of the
rocker d' on cylinder A¹ to the right in the figures, thus moving the upper side of
the rocker to the left, which oscillates the rocker c¹ on its pivot 5, which is now
stationary, except as the link 17 may swing on the lever e¹, as the piston X' is
at the end of its stroke, and the lever e¹ held stationary. This movement of the
rocker c, through link 13 and crank 12 on valve a', at the left end of the cylin-
der A', oscillates this valve, so as to open it for the admission of steam to the left
end of the cylinder A¹, while it actuates the valve a¹ at the right end of the
cylinder slightly, but not enough to open the port 1, the link 13 at this end of the
cylinder swinging during this movement nearly in the arc of a circle from its
pivot to the link 12. This movement of the rocker d', through links. 15 and
crank arms 14, on exhaust valves b¹, also shifts these exhaust valves, so as to
close the exhaust port at the left end of cylinder A', and open that at the right
end of the cylinder for the reversal of the piston X'. The piston X' now moves
to the right, while the piston X completes its stroke to the left, and at the proper
points in its stroke the piston X', through its crosshead, link 18, lever e¹, and
link 17, rocks the rocker c on cylinder A' to the right on its pivot 4, so as to
oscillate valve a¹ at the left end of the cylinder, to cut off the steam behind the
piston X, in the same manner as previously described in connection with pis-
ton X, and after the piston X has completed its stroke to the left, to move the
rocker d on cylinder A, through link 22, lever N¹, rock shaft T, crank 21, and
link 20, so as to rock the rocker c on its pivot 5, and open valve a, at the left end
of the cylinder, and, at the same time, to shift the exhaust valves b, in the same
manner as previously described in connection with the action of piston X upon
the valves of cylinder A¹. Thus, the cycle of operations is continued in the
operation of the engine.
pro-
When it is desired to run the engine low duty, that is, without the cut off, and
admitting steam throughout the stroke, the rockers c, c¹ may be detached from
the pistons, and secured in any suitable manner, so as to hold the pivots
perly for the required action of the rockers c, c¹ by the rockers d, d. Thus, the
levers e, e¹ may be detached from the cross-heads, and secured in central position,
as shown in dotted lines in Figure 1. These levers e, e¹ may be held in this
position by pins, or any other suitable means, or the links 17 may be detached
from the levers e, e¹, and pivoted at fixed points on suitable supports, the levers e,
then swinging idly, or being removed.
Referring now to the parts of the improved apparatus shown in Figures 1 to 3,
for supplying the compensating cylinders with fluid under pressure, through
pipe I, and securing the desired operation of the construction, the force main E
is connected by a pipe J with the lower chamber k of a vertical accumulator
cylinder K, on one side of the differential piston L, so as to transmit the force
pressure to the smaller end of the piston, and the opposite or larger end of the
piston is under air pressure in the chamber k¹ at the top of the cylinder, and con-
nected by pipe M with the upper chamber o¹ of a similar vertical accumulator
cylinder O, having therein the differential piston P, the larger upper end of
the piston P being subjected to the air pressure in the cylinder chamber o¹ and
pipe M, and the lower smaller end of the piston P transmitting the pressure
through the lower chamber o of the cylinder. O to pipe I, which connects there-
with, and thus to pipes H and the compensating cylinders G G¹, the compen-
sating cylinders, pipes H, I, and the chamber o, being filled with any suitable
liquid, such as water or oil, for the operation of the compensating cylinders.

page_text: The air system, consisting of the upper chambers k¹, o¹, of the cylinders K, O,
and the connecting pipe M, are supplied with air through a pipe Q from an air
compressor R, which may be of any suitable construction, and this air system
is preferably enlarged, so as to secure a large air capacity, without enlarging
the cylinders K, O for that purpose, by an air tank U, which may be placed at
any suitable point, and is shown as connecting to the. pipe A by pipe V. The
pistons L and P are shown as single differential pistons, but it will be understood
that this is not essential, and that any suitable arrangement of cylinders and
pistons may be used to secure the desired result, and that the differential action
may be secured by a proper single piston, or by two pistons connected in any
suitable manner.
Referring now to the details of the construction, the cylinder K may be and
is shewn as being substantially the same in construction as accumulator cylinders
heretofore used, but it may be of any suitable construction, so as to secure the
application of the force main pressure through the pipe J to one side of the
differential piston L, and the transmission of this pressure through the body of
air or other elastic fluid opposing the piston on the opposite side. The pipe J is
preferably provided with a suitable valve 23, by which the compensating con-
struction can be cut off from the force main when necessary. The upper cham-
ber of the cylinder K is preferably provided with a pipe 24, as shown, which is
located at such a point that the piston L passes this pipe in descending, before
striking the bottom cylinder head, so that the air will escape from the space
above the piston through pipe 24, as the latter passes this pipe, and thus quickly
relieve the system of pressure, in case the force main pressure should suddenly
fall below the normal.
The piston L carries a pipe 25, which extends through the chamber and the
upper head of the cylinder, being packed therein in any suitable manner, and
is provided at the top with an escape valve or cock 26, which is normally open,
and with one or more openings 27 along the pipe, which are outside the cylinder,
when the piston is in the upper part of the cylinder chamber, but are moved
below the cylinder head, and inside the cylinder chamber, when the piston
descends into the lower part of the cylinder chamber, so as to then permit the pas-
sage of air through these openings and cock 26. Any other suitable means may
be used by, which the position of the piston controls the escane of air from the
chamber k, so as to secure the result hereafter described, but the construction-
shown is simple and efficient, and is preferably used.
The piston L preferably closes the port of pipe M before it reaches the top of
the cylinder chamber k¹, so as to cushion the piston, to prevent striking the
cylinder head, and a pipe 28, is preferably used connecting the top of the cylinder
chamber with the air pipe Q from the compressor R, so as to permit air to be
admitted to the cylinder chamber above the piston L, after the latter has
closed pipe M, this pipe 28 being controlled by a cock 29. A cock 30 is also used
on the pipe Q, between the air compressor and the air system supplied thereby,
so that the air compressor may be cut off the air system when desired, as ex-
plained hereafter. The pipe M is also preferably provided with throttle
valves 31, 32, on opposite sides of the connection of pipe M with pipes Q, V, and
between such connection and the respective cylinders K, O, so that by these
throttle valves one or both of the cylinders may be cut out, or the air system
otherwise controlled.
The cylinder and piston P are shewn as similar in construction to cylinder K
and piston L, but may be of any other suitable construction, to secure the desired
transmission of pressure to the compensating cylinders. With this cylinder and
piston are shown means which are preferably used for adjusting the power pro-
duced by the accumulator, by pressure applied to counterbalance the pressure on
the upper end of the accumulator piston, as follows:-An air tank W is. used,
which is preferably of circular form, as shown, enclosing and supporting the
lower end of the cylinder O, although it may be arranged otherwise, and this

page_text: tank W is connected by a pipe 33 with the upper chamber o' of cylinder O, below
the piston P therein, so that the pressure of the air in tank W is opposed to the
pressure on the opposite side of the piston, and the power developed by the latter
through the lower end of the piston acting upon the liquid of the lower chamber
of the cylinder and pipe I, reduced according to the counterbalancing pressure
from tank W. Pipe 33 is shown as connected by pipe 34, controlled by cock 35,
with the air chamber at the upper end of the cylinder O, although it will be
understood that the tank W may be supplied with air from any other part of
the system. An outlet pipe 36, provided with a safety valve, is preferably used
in connection with pipe 33, so as to permit the air to blow out, in case of excess
of pressure.
The piston P, preferably carries a pipe 37, extending through the head of the
cylinder, and suitably packed, this pipe carrying, at its upper end, a cock 38,
normally closed, and having at its lower end one or more openings 8.
This pipe
serves as a gauge to show the position of the piston P, as in the case of the pipe 25
on piston L, and, by opening cock 38 also, oil or water that may be used, or may
collect on the top of the piston P, may be blown out. The air tank W is also
preferably provided with a blow-off pipe 39, provided with a cock, by opening
which, any oil or water collected in the tank W may be blown out, and the pres-
sure in the tank W may thus also be reduced by opening the cock, and per-
mitting the air to escape.
The operation of this part of the apparatus will be understood from a brief
description:
Let it be assumed that the engine is in operation, and that the normal or
ordinary pressure exists in the main E, and in the air system, and that the pistons
of the cylinders A, B, are commencing their stroke towards the water cylinders.
During the first half of the stroke, the liquid will be forced out of the compen-
sating cylinders G, into the cross connection pipes H, and through the pipe I
into the chamber o at the lower end of the cylinder O, where it will act upon
the smaller end of the plunger P' in said chamber, and raise the plunger against the
pressure of the air in chamber o¹, and the air system, and indirectly through
the air system and piston L, upon the liquid in the force main, through the
smaller end of the piston L in chamber k and pipe J. During the latter half of
the stroke, the operation will be reversed, and the plunger P, acted upon by the
pressure from the force main, acting indirectly through the air system, will move
downward, and force the liquid out of chamber o in cylinder O into pipes I, H,
and the compensating cylinders G, thus giving back the power which was ex-
pended in raising the plunger P. The power exerted upon the plunger F in
water cylinder C is thus maintained to the end of the stroke, although the ad-
mission of steam to the steam cylinders A, B has been cut off at the point in the
stroke for which the construction is adjusted, by the movement of the pistons
acting through the lever e and connections to rockers c, and the valves, as fully
described above.
As the pistons of the cylinders A, B approach the end of their stroke, they
will operate the valves of the cylinders A', B₁ on the opposite side of the engine,
through cross-over shaft S, and connections to the rockers d' and the valves, so
as to start the pistons of cylinders A¹, B', upon their stroke in the same direction
as the pistons of cylinders A, B are then moving. During this stroke of the
pistons of cylinders A¹, B', the operation just described will be repeated in con-
nection with the compensating cylinders G¹, the compensating cylinders G thus
giving out power, and the compensating cylinders G₁ storing up power during
the remainder of the stroke of the pistons in the cylinders A, B, and as the
pistons of the cylinders A B₁ pass half-stroke, the compensating cylinders G¹
will, in turn, give back the power thus stored up thereby, the admission of steam
to the cylinders A', B¹ being cut off at the proper point by the pistons acting
through the lever e¹ and connections to the rockers and the valves. The pis-
tons of cylinders A, B will reach the end of their stroke and rest until, as the

page_text: pistons of cylinders A', B₁ approach the end of their stroke, the latter will operate
the valves of cylinders A, B through cross over shaft T and the connections to
rockers d and the valves, so as to start the pistons of cylinders A, B, upon their
return stroke, the compensating cylinders G then storing up power, and the
compensating cylinders G¹ giving back power during the rest of the stroke of
the pistons of cylinders A', B', all as fully described above. The operation will
thus continue during the normal running of the engine.
It will be seen that this operation of the compensating cylinders would result
in producing pulsations in the column of fluid in the force main and shock
in the engine and apparatus, if the pressure were transmitted between the cylin-
ders and force main directly, or through an inelastic medium, and that sudden
changes of pressure in the force main would be transmitted to, and cause sudden
and injurious changes in, the action of the compensating cylinders upon the
engine. The elastic cushion between the pistons L, P, formed by the air system,
prevents these results, and secures a smooth and uniform operation of the engine,
without shock or pulsations in the force main, the elasticity of the air resulting
in the gradual transmission of changes in pressure, and the absorption of the
pulsations that otherwise would result, while at the same time the compensating
cylinder pressure is controlled by, and conforms to, the load on the engine, so
that the power developed by the compensating cylinders increases with the load.
as in starting the engine, whenever the force main has become empty or partly
empty, or on pipe lines, where the load depends on the friction, and thus on the
velocity of the column of liquid. In case of breakage of the force main, also,
the pressure upon the compensating cylinders will be immediately relieved, as
the pressure in the air system is dependent upon the pressure in the force main,
and the compensating cylinders will at once cease to develop more power than is
necessary to overcome the reduced load on the plungers.
When used where the force-main pressure and other running conditions are
substantially uniform, the air compressor R may be cut off the system by closing
cock 30, when the desired air pressure in the system is secured after starting the
engine, the air compressor R then being operated only at intervals, as required,
to supply air leakage, or when it is desired to increase the air pressure, for any
reason. In starting the engine, however, and when the main pressure is liable
to sudden or considerable variations, it is preferable to run the air compressor
on the air system continuously, the apparatus then being. self-adjusting, to secure
the desired air pressure and operation under different force pressures, or other
changes in running conditions producing changes of pressure in the system.
This operation is as follows:-
Let it be again assumed that in the position of parts shewn in the drawings,
the air compressor R is pumping continuously into the air system, so as to
increase the pressure therein, the pressure in the force main acting on the lower
end of the differential piston L having just been increased, so that the piston
is raised into the position shown, with the openings 27 in pipe 25 outside the
cylinder chamber k¹, and no air is escaping from chamber through this pipe.
Under the continuous pumping of the air compressor R, the piston L will be
forced downward, if the pressure in the force main remains constant, so that
when the desired pressure in the air system corresponding to the actual pressure
in the force main, and the normal position for which piston L is adjusted, is
reached, one or more of the openings 27 will connect the chamber k¹ with the
pipe 25, and air thus be permitted to escape from the chamber and the air
system, so that the pressure within the system is not further increased, or the
piston L moved downward further, but the excess of air pumped by the com-
pressor R escapes through the pipe 25. In case of a further decrease of the
pressure in the force main, the downward movement of the piston L, under
the pressure in the chamber k, will bring more of the openings 27 within the
chamber k, and thus the air will escape more rapidly from the chamber k¹, until
he pressure in the air system is thus reduced to correspond to the reduced force.

page_text: main pressure, and the normal position of the piston L, with the excess of air
pumped escaping through the pipe 25 is again secured. In case of a breakage
of the main, or sudden large decrease of pressure therein, producing a larger
movement of the piston L, the air pressure in chamber k, and the air system,
will be relieved through pipe 24, as the piston L passes below this pipe, so that
the pressure is removed before the piston could reach the cylinder head, and the
piston also is preferably cushioned by the air below it, being partially confined
in the space between the pipe 24 and the cylinder head.
With the air compressor R pumping continuously into the air system, and the
piston L, in such position that the excess of air pumped by the air compressor R
escapes through openings 27 in pipe 25, if the pressure in the force main be
suddenly or largely increased, the piston L will be raised, so as to move the
pipe 25 upward, and close the openings 27, by moving them into or outside the
packing gland in the cylinder head, and the continuous delivery of the air to
the system by the air compressor R will then operate to gradually increase the
pressure in the air system, to correspond to the increased pressure in the force
main, and move the piston L downward again to normal position. As the
piston L is moved upward against the pressure of the air system by increase of
pressure in the force main, it will close the port of pipe M before it can strike
the top cylinder head, so that the further passage of air from the chamber is
thus prevented, and an air cushion formed between the piston L and the top of
the cylinder, thus avoiding danger of injury by the piston striking the cylinder
head. In case of such an increased pressure in the main, and its continuance,
so that the piston L is not again lowered by the pressure of the air confined
between the cylinder L and the cylinder head, the cock 29, which preferably will
always be slightly opened, will admit air from the air system and compressor
through pipe 28 to the chamber k¹, above the piston, and the pressure in the
chamber, thus be increased, to move the piston L downward again.
It will be seen that the air system, with the continuously operating air com-
pressor, is thus self-adjusting to changes in main pressure, and that, after
starting the engine with the compressor R in operation, the pressure in the air
system required for the existing main pressure is soon attained, this being
determined by the construction itself in actual operation. When this point is
reached, however, it is obvious that, if the force pressure and other running
conditions are uniform, the air compressor R may then be cut out of the system
by closing the cock 30, and the air compressor then operated only as required
to maintain the desired pressure, the pressure existing in the system being shown
by any suitable pressure gauge, and the position and operation of the
pistons L, P, being indicated by the pipes 25, 37. On opening the cock 30, the
desired pressure in the system will be automatically secured, to correspond to
the pressure in the force main, the cock 30 then being closed again. It will be
understood, also, that such an air system may be used, without any means for
permitting the escape of air, so as to automatically secure the required pressure
corresponding to the main pressure.
The power developed by the accumulator may readily be adjusted by increasing
or decreasing the counterbalancing pressure applied to piston P, from tank W,
and exactly the desired development of power by the compensating cylinders
relatively to the pressure in the force main be thus secured, so that the con-
struction shewn may be used with force pressures differing widely, and exactly
the desired position secured, without change of parts of the accumulator pistons,
to adjust the power. A comparatively large air system is preferably used, so as
to secure a large elastic cushion for the absorption of pulsations, and an air tank,
as U, is preferably employed to secure this result, without inconveniently large
air cylinders. It will be understood, however, that such separate air tank may
be omitted, and that the air cushion may be of any desired size.
The use of the differential pistons shewn is not absolutely essential to securing
the desired operation, and their size and arrangement will depend somewhat

page_text: upon the conditions of use, but differential pistons with the air pressure applied
to the larger ends, or equivalent constructions, are preferally used, so that the
air pressure maintained in the system need not be as high as the force pressure.
In the construction shewn in Figures 1 to 3, the cylinder K or O may be cut
off the system, by closing cock 31 or 32, and the cylinder K used only as an air
cushion for the force main, or the compensating cylinders and accumulator O,
can be run independently of the force main, if desired, for any purpose.
It will be understood that this part of the invention, relating to the trans-
mission of the pressure from the force main to the compensating cylinders,
broadly considered, is not limited to the use of a plurality of cylinders with the
pressure transmitted between their pistons through an elastic cushion, but that
other suitable constructions may be used with one or more cylinders operating
on the same principle, and including the features claimed hereafter. This part
of the invention is especially applicable in connection with pumping engines
used on oil lines, and has been designed in connection therewith, although it
will be understood that it is of general application. In oil pipe lines, the
pressure is usually very high, so that it is necessary to reduce the main pressure
considerably, in applying it to the compensating cylinders, especially through the
medium of air pressure, owing to the practical difficulty of using air under as
high pressure as that of the main pipe line, and in such constructions, also, it
is especially important that the compensating pressure should be dependent on
the force pressure, but the latter not be directly transmitted to the compensating
cylinders. The present invention makes it possible to secure the proper pressure
in the compensating cylinders corresponding to, and dependent on, the pressure
in the force main, while at the same time pulsations in the force main, or
shock in the system, are avoided, under wide variations of pressure, and different
running conditions. This construction also effectually prevents the passage of
oil or dirt from the pipe line to the compensating cylinders, and the compen-
sating power may readily be adjusted as desired.
While the improved valve movement and apparatus for transmitting pressure
to the compensating cylinders are preferably combined, a greatly improved high-
duty pumping engine being thus provided, and the present invention consists,
in part, of constructions combining the two parts of the invention in such a
complete apparatus, it will be understood that the means for controlling the
pressure in the compensating cylinders may be used with engines employing a
valve movement of any other suitable form.
The improved valve movement also may be used in engines not employing
compensating cylinders, although in direct-acting engines such cylinders are
preferably used, co-acting with the steam pistons in securing the full stroke of
the latter, after the steam or other motor fluid is cut off by the valve movement.
In constructions in which compensating cylinders are employed, also, the
improved valve movement may be used with the pressure supplied to the com-
pensating cylinders from any suitable source, and through other connections
than those shown in Figures 1 to 3. In pumping engines employing the im-
proved valve movement and compensating cylinders, however, the pressure in
the compensating cylinders is preferably derived from the force main, and an
accumulator is preferably employed between the force main and compensating
cylinders, and a very efficient construction is secured in some pumps, by con-
necting the force main side of the accumulator piston to the air chamber usually
employed on the force main in such pumping engines.
In Figure 4, such a construction is shown, in which the improved valve move-
ment is applied in connection with a triple-expansion duplex pumping engine,
with an air chamber on the force main, the connections for the compensating
cylinders G, G¹, being the same as shewn in Figures 1 to 3, except that the
pipe M from accumulator cylinder O is connected directly to the air chamber
on the force main, so that the pressure in the compensating cylinders is derived
from the force main through the air chamber and accumulator cylinder O, instead

page_text: of being taken from the force main through the two pistons L and P, and
interposed air system previously described.
The operation of this triple expansion pumping engine shewn in Figure 4 will
be readily understood from the previous description of the action of the improved
valve movement and of the compensating cylinders, the valve movement on the
third cylinders C, C₁, in this construction, having the same connections and
action as the valve movements on the second cylinders B, B', in the construction
shewn in Figures 1 to 3, and the operation of the compensating cylinders G, G¹,
and the accumulator cylinder O, being the same as usual, and as described in
connection with the construction shewn in Figures 1 to 3, and the pressure in
the compensating cylinders being regulated by adjusting the pressure on the
underside of the piston P in cylinder O, in the same manner as previously
described.
While the rockers and connections for operating th valves in the improved
valve movement have been shown and described as applied to a duplex engine,
and the invention consists, in part, of features in such constructions, it will be
understood that this part of the invention, broadly considered, is applicable in
other classes of engines, and that the rocker connected to the valves may be
actuated for securing the required movement of the valves by any suitable means,
either from the pistons of the different cylinders in multiple cylinder engines,
or by any suitable devices in single engines. In the preferred construction,
separate exhaust valves are employed, but the invention, considered broadly, is
applicable also in engines of that well-known class in which a single valve
controls the admission, exhaust, and cut-off. It will be understood, also, that the
improved valve movement may be used with valves of different form and move-
ment from those shown, and with slide valves as well as oscillating valves, and
that many other modifications may be made in the constructions illustrated,
without departing from the invention, which is not to be limited to the exact
form or arrangement of the devices shown.
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 from abroad), I declare that what I claim is:-
1. The combination with an engine cylinder, and a single valve at each end
of the cylinder controlling the admission and cut-off of the motor fluid, of a
rocker having two pivots, connections from the rocker to the valves, and means
of oscillating the rocker on one of its pivots for operating the valves for admis-
Bion, and on the other pivot for operating the valves for cut off, substantially as
described.
2. The combination with an engine cylinder, and a single valve at each end
of the cylinder controlling the admission and cut off of the motor fluid, of a
rocker connected to the valves, a movable member on which the rocker is pivoted,
means for operating the movable member, to oscillate the rocker for operating
the valves for admission, and means for oscillating the rocker on its pivot to
the movable member, for operating the valves for cut off, substantially as
described.
3. The combination with an engine cylinder, and a single valve at each end
of the cylinder controlling the admission and cut-off of the motor fluid, of a
rocker connected to the valves, a second rocker on which said rocker is pivoted,
means for actuating said second rocker, to oscillate the first mentioned rocker
for operating the valves for admission, and means for oscillating the first-
mentioned rocker on its pivot to the second rocker, for operating the valves for
cut off, substantially as described.
4. The combination with an engine cylinder and a single valve at each end
of the cylinder controlling the admission and cut-off of the motor fluid, of a
rocker connected to the valves, a movable member on which the rocker is
pivotted, actuating means having a pivotal connection to the rocker, for oscil-

page_text: lating said rocker on the movable member, for operating the valves for cut off,
said actuating means being detachable, and adapted to be secured in a fixed
position, for the operation of the valves without cut off, and means for actuating
said movable member, to oscillate the rocker on its pivotal connection to the
actuating means for operating the valves for admission, substantially as
described.
5. The combination with two cylinders and a single valve at each end of each
cylinder controlling the admission and cut off of the motor fluid, of a rocker for
each cylinder, connections between the rocker of each cylinder and the valves of
its cylinder through which each of said valves is operated by said rocker for
admission and cut off, and connections between the rocker of each cylinder and
the pistons of both the cylinders, all combined and operating to actuate the
valves of each cylinder through said rocker by the piston of the other cylinder,
to admit the motor fluid, and, through the same rocker, by its own piston to cut
off the motor fluid, substantially as described.
6. The combination with two cylinders, and a single valve at each end of each
cylinder controlling the admission and cut off of the motor fluid, of a rocker for
each cylinder having two pivots, separate connections from each rocker to the
respective valves of its cylinder, and connections between each of said rockers
and the pistons of both of the cylinders for oscillating the rockers on their
respective pivots for operating the valves for admission and cut-off, substantially
as described.
7. The combination with two cylinders and single valves controlling the
admission and cut off of the motor fluid, of a rocker for each cylinder connected
to the valves of its cylinder, a movable member for each cylinder on which the
rocker is pivotted, connections between each of said movable members and the
piston of the other cylinder, and connections between each of said rockers and
the piston of its own cylinder, all combined and operating to actuate the valves
of each cylinder by the piston of the other cylinder, to admit the motor fluid,
and, by its own piston, to cut off the motor fluid, substantially as described.
8. The combination with two cylinders and single valves controlling the
admission and cut off of the motor fluid, of a rocker for each cylinder connected
to the valves of its cylinder, a movable member for each cylinder on which the
rocker is pivotted, connections between each of said movable members and the
piston of the other cylinder, and connections between each of said rockers and
the piston of its own cylinder, all combined and operating to actuate the valves
of each cylinder by the piston of the other cylinder, to admit the motor fluid,
and, by its own piston, to cut off the motor fluid, separate exhaust valves, and
operating connections between said exhaust valves and the movable members,
substantially as described.
9. The combination with two cylinders and single valves controlling the
admission and cut off of the motor fluid, of a rocker for each cylinder connected
to the valves of its cylinder, a second rocker for each cylinder on which the first
mentioned rocker is pivotted, connections between each of said first-mentioned
rockers and the pistons, of both the cylinders, connections between each of said
second rockers and the pistons of the other cylinder, and connections between
each of said first-mentioned rockers and the piston of its own cylinder, all
combined and operating to actuate the valves of each cylinder by the piston of
the other cylinder, to admit the motor fluid, and, by its own piston, to cut off the
motor fluid, substantially as described.
10. The combination with two cylinders and single valves controlling the
admission and cut-off of the motor fluid, of connections between each of said
valves and the pistons of both cylinders, whereby the valves of each cylinder are
actuated by both of the pistons for the operation of the valves with cut-off, the
connections between each of the valves and one of the pistons being adapted to
be secured in a fixed position, for the operation of the valves without cut-off,
substantially as described.

page_text: 11. The combination with two cylinders and single valves controlling the
admission and cut-off of the motor fluid, of a rocker for each cylinder having
two pivots and connections between said pivots and the respective pistons,
whereby the rocker is rocked on one of its pivots by one of the pistons, and on
the other of said pivots by the other piston, and connections between said rockers
and the valves, all combined and operating to actuate the valves of each cylinder
by one of the pistons, to admit the motor fluid, and, by the other piston, to cut
off the motor fluid, the cut-off connections between the rockers and pistons being
adapted to be secured in a fixed position for the operation of the valves without
cut-off, substantially as described.
12. The combination with the main cylinder or cylinders and piston or pistons
and single valves at each end of the cylinder or cylinders controlling the admis-
sion and cut-off the motor fluid, of a rocker for each cylinder having two pivots,
connections from each rocker to the valves of its cylinder, means for oscillating
each rocker on one of its pivots, for operating the valves for admission, and on
the other pivot for operating the valves for cut-off, and a compensating cylinder
or cylinders and piston or pistons arranged to act in opposition to the main
piston or pistons during the first part of the stroke, and in conjunction therewith
during the last part of the stroke, substantially as described.
13. The combination with the main cylinder or cylinders and piston or pistons
and single valves at each end of the cylinder or cylinders controlling the admis-
sion and cut-off of the motor fluid, of a rocker for each cylinder having two
pivots, connections from each rocker to the valves of its cylinder, means for
oscillating each rocker on one of its pivots, for operating the valves for
admission, and on the other pivot for operating the valves for cut-off, a com-
pensating cylinder or cylinders and piston or pistons arranged to act in
opposition to the main piston or pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, and an accumular
arranged between the compensating cylinder or cylinders and the source from
which the pressure in said cylinder or cylinders is derived, substantially as
described.
14. The combination of the main cylinder or cylinders and piston or pistons
and single valves at each end of the cylinder or cylinders controlling the
admission and cut-off of the motor fluid, of a rocker for each cylinder having two
pivots, connections from each rocker to the valves of its cylinder, means for
oscillating each rocker on one of its pivots, for operating the valves for admission,
and on the other pivot for operating the valves for cut-off, a compensating
cylinder or cylinders and piston or pistons arranged to act in opposition to the
main piston or pistons during the first part of the stroke, and in conjunction
therewith during the last part of the stroke, and two pistons arranged between
the compensating cylinder or cylinders and the source from which the pressure
in said cylinder or cylinders is derived, and a body of elastic fluid between said
pistons, substantially as described.
15. The combination with the main cylinder or cylinders, and piston or pistons.
of a pumping engine, and single valves at each end of the cylinder or cylinders
controlling the admission and cut-off of the motor fluid, of a rocker for each
cylinder having two pivots, connections from each rocker to the valves of its
cylinder, means for oscillating each rocker on one of its pivots, for operating the
valves for admission, and on the other pivot for operating the valves for cut-off,
a compensating cylinder or cylinders and piston or pistons arranged to act in
opposition to the main piston or pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, and an accumulator
between the compensating cylinder or cylinders and the force main, through
which pressure is transmitted from the force main to said compensating cylinder
or cylinders,, substantially as described.
16. The combination with the main cylinder or cylinders and piston or pistons
of a pumping engine, and single valves at each end of the cylinder or cylinders

page_text: controlling the admission and cut-off of the motor fluid, of a rocker for each
cylinder having two pivots, connections from each rocker to the valves of its
cylinder, means for oscillating each rocker on one of its pivots for operating the
valves for admission, and on the other pivot for operating the valves for cut-off,
a compensating cylinder or cylinders and piston or pistons, arranged to act in
opposition to the main piston or pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, two pistons between
the said compensating cylinder or cylinders and the force main, through which
pressure is transmitted from the force main to said compensating cylinder or
cylinders, and a body of elastic fluid between said pistons, substantially as
described.
17. The combination with the main cylinders and pistons forming the two sides
of a duplex engine, and single valves at the ends of the cylinders controlling the
admission and cut-off of the motor fluid, of a rocker for each cylinder, connections
between each of said rockers and the valves of its cylinder, for actuating said
valves by said rocker for admission and cut-off, and connections between each of
said rockers and the pistons on both sides of the engine, all combined and
operating to actuate the valves of each side of the engine by the piston on the
other side, to admit the motor fluid, and, by the piston of their own side, to cut
off the motor fluid, and a compensating cylinder or cylinders and piston or pistons
for each side of the engine, arranged to act in opposition to the main pistons
during the first part of the stroke, and in conjunction therewith during the last
part of the stroke, substantially as described.
18. The combination with the main cylinders and pistons forming the two
sides of a duplex engine, and single valves at the ends of the cylinders con-
trolling the admission and cut-off the motor fluid, of a rocker for each cylinder,
connections between each of said rockers and the valves of its cylinder, for
actuating said valves by said rocker of admission and cut-off, and connections
between each of said rockers and the pistons on both sides of the engine, all
combined and operating to actuate the valves of each side of the engine by the
piston on the other side, to admit the motor fluid, and, by the piston of their own
side, to cut off the motor fluid, a compensating cylinder or cylinders and piston
or pistons for each side of the engine, arranged to act in opposition to the main
pistons during the first part of the stroke, and in conjunction therewith during
the last part of the stroke, and an accumulator between the compensating
cylinders and the source from which the pressure in said cylinders is derived,
substantially as described.
19. The combination with the main cylinders and pistons forming the two
sides of a duplex pumping engine, and single valves at the ends of the cylinders
controlling the admission and cut-off of the motor fluid, of a rocker for each
cylinder, connections between each of said rockers and the valves of its cylinder,
for actuating said valves by said rocker for admission and cut-off, and con-
nections between each of said rockers and the pistons on both sides of the engine,
all combined and operating to actuate the valves of each side of the engine by
the piston on the other side, to admit the motor fluid, and, by the piston of their
own side, to cut off the motor fluid, a compensating cylinder or cylinders and
piston or pistons for each side of the engine arranged to act in opposition to the
main pistons during the first part of the stroke, and in conjunction therewith
during the last part of the stroke, and an accumulator between said compensating
cylinders and the force main, through which pressure is transmitted from the
force main to said compensating cylinders, substantially as described.
20. The combination with the main cylinders and pistons forming the two
sides of a duplex pumping engine, and single valves at the ends of the cylinders
controlling the admission and cut-off of the motor fluid, of a rocker for each
cylinder, connections between each of said rockers and the valves of its cylinder,
for actuating said valves by said rocker for admission and cut-off, and connections
between each of said rockers and the pistons on both sides of the engine, all

page_text: combined and operating to actuate the valves of each side of the engine by the
piston on the other side, to admit the motor fluid, and, by the piston of their own
side, to cut off the motor fluid motor fluid, a compensating cylinder or cylinders
and piston or pistons for each side of the engine, arranged to act in opposition to
the main pistons during the first part of the stroke, and in conjunction therewith
during the last part of the stroke, two pistons between said compensating
cylinders and the force main, through which pressure is transmitted from the
force main to said compensating cylinders, and a body of elastic fluid between
said pistons, substantially as described.
21. The combination with a main cylinder or cylinders and piston or pistons,
and a compensating cylinder or cylinders and piston or pistons arranged to act
in opposition to the main piston or pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, of two pistons
arranged between the compensating cylinder or cylinders and the source from
which the pressure in said cylinder or cylinders is derived, and an elastic cushion
between said pistons, substantially as described.
22. The combination with a main cylinder or cylinders and pistons or piston,
and a compensating cylinder or cylinders and piston or pistons arranged to act
in opposition to the main piston or pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, of two pistons
arranged between the compensating cylinder or cylinders and the source from
which the pressure in said cylinder or cylinders is derived, and a body of elastic
fluid between said pistons, substantially as described.
23. The combination with a main cylinder or cylinders and piston or pistons,
and a compensating cylinder or cylinders and piston or pistons arranged to act
in opposition to the main piston or pistons during the first part of the stroke,
and in conjunction therewith during the last part of the stroke, of two cylinders
and pistons arranged between the compensating cylinder or cylinders and the
source from which the pressure in said cylinder or cylinders is derived, one of
said pistons being subjected, on one side, to the pressure of the fluid from said
source, and the other of said cisterns, on one side, to the pressure of the fluid
in the compensating cylinder or cylinders, connections between said cylinders
on the other side of said pistons, and a body of elastic fluid filling said chambers
and connections through which pressure is transmitted between said pistons,
substantially as described.
24. The combination with the main cylinders and pistons forming the two sides
of a duplex engine, and having connections by which the valve or valves of each
side is or are operated from the other side, and a compensating cylinder or
cylinders and piston or pistons for each side of the engine, arranged to act in
opposition to the main pistons during the first part of the stroke, and in con-
junction therewith during the last part of the stroke, of two pistons arranged
between the compensating cylinders and the source from which the pressure in
said cylinder or cylinders is derived, and a body of elastic fluid between said
pistons. substantially as described.
25. The combination with the main cylinder or cylinders and piston or pistons
of a pumping engine, and a compensating cylinder or cylinders and piston or
pistons arranged to act in opposition to the main piston or pistons during the
first part of the stroke, and in conjunction therewith during the last of the stroke,
of a piston between said compensating cylinder or cylinders and the force main,
subjected on one side to the pressure in the force main, and a body of elastic
fluid acting on the opposite side of said piston, through which pressure is
transmitted from the force main to the compensating cylinder or cylinders,
substantially as described.
26. The combination with the main cylinder or cylinders and piston or pistons
of a pumping engine, and a compensating cylinder or cylinders and piston or
pistons arranged to act in opposition to the main piston or pistons during the
first part of the stroke, and in conjunction therewith during the last part of the

page_text: stroke, of two pistons between said compensating cylinder or cylinders and the
force main, through which pressure is transmitted from the force main to said
compensating cylinder or cylinders, and a body of elastic fluid between said
pistons, substantially as described.
27. The combination with the main cylinder or cylinders and piston or pistons
of a pumping engine, and a compensating cylinder or cylinders and piston or
pistons arranged to act in opposition to the main piston or pistons during the
first part of the stroke, and in conjunction therewith during the last part of the
stroke, of two differential pistons arranged between the compensating cylinder
or cylinders and the force main, through which pressure is transmitted from
the force main to the said compensating cylinder or cylinders, said pistons being
subjected on one side, respectively, to the pressure of the fluid in the force main
and in the compensating cylinder or cylinders, and a body of elastic fluid between
the other sides of said pistons, substantially as described.
28. The combination with the main cylinders and pistons forming the two
sides of a duplex pumping engine, and having connections by which the valve
or valves on each side is or are operated from the other side, and a compensating
cylinder or cylinders and piston or pistons for each side of the engine, arranged
to act in opposition to the main pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, of a piston between
said compensating cylinders and the force main, subjected on one side to the
pressure in the force main, and a body of elastic fluid acting on the opposite side
of said piston, through which pressure is transmitted from the force main to the
compensating cylinders, substantially as described.
29. The combination with the main cylinders and pistons forming the two
sides of a duplex pumping engine, and having connections by which the valve or
valves on each side is or are operated from the other side, and a compensating
cylinder or cylinders and piston or pistons for each side of the engine, arranged
to act in opposition to the main pistons during the first part of the stroke, and
in conjunction therewith during the last part of the stroke, of two pistons
between said compensating cylinders and the force main, through which pressure
is transmitted from the force main to said compensating cylinders, and a body of
elastic fluid between said pistons, substantially as described.
30. The combination with a pumping engine having one or more compensating
cylinders and pistons, of connections between said compensating cylinder or
cylinders and the force main, including a piston acted upon on one side directly
by the liquid in the force main, and a body of elastic fluid acting on the opposite
side of the piston, and through which pressure is transmitted from the force
main to the compensating cylinder or cylinders, substantially as described.
31. The combination with a pumping engine having one or more compensating
cylinders and pistons, of connections between said compensating cylinder or
cylinders and the force main, including a piston subjected on one side to the
pressure in the force main, a second piston having one end subjected to the
pressure in the compensating cylinder or cylinders, a body of elastic fluid between
said pistons, through which pressure is transmitted from the force main to the
compensating cylinder or cylinders, and means for applying adjustable pressure
to said second piston independently of said body of elastic fluid, to regulate the
pressure in the compensating cylinder or cylinders, substantially as described.
32. The combination with a pumping engine having one or more compensating
cylinders and pistons, of connections between said compensating cylinder or
cylinders and the force main, including a piston subjected on one side to the
pressure in the force main, a body of elastic fluid acting on the opposite side of
the piston, and through which pressure it transmitted from the force main to
the compensating cylinder or cylinders, and means controlled by said piston for
permitting the escape of elastic fluid from said body of fluid, when the piston is
moved against the force pressure beyond a certain point, substantially as
described.

page_text: 33. The combination with a pumping engine having one or more compensating
cylinders and pistons, of a piston subjected, on one side, to the pressure in the
force main, a second piston subjected, on one side, to the pressure in the com-
pensating cylinder or cylinders, a body of elastic fluid between said pistons, a
continuously operating pump for supplying the elastic fluid, and means controlled
by the position of the first-mentioned piston, to permit the escape of elastic fluid,
and prevent its escape, to secure the proper pressure of the elastic fluid under
changes of main pressure, substantially as described.
34. The combination with a pumping engine having one or more compensating
cylinders and pistons, of a piston subjected, on one side, to the pressure in the
force main, a second piston subjected, on one side, to the pressure in the com-
pensating cylinder or cylinders, a body of elastic fluid between said pistons,
through which pressure is transmitted from the force main to the compensating
cylinder or cylinders, and means controlled by the first mentioned piston, to
permit the escape of elastic fluid from between the pistons, when said first-
mentioned piston is moved against the force pressure beyond a certain point, and
to prevent the escape of elastic fluid when the piston is moved in the opposite
direction beyond a certain point, substantially as described.
35. The combination with a piston acted upon by a column of liquid under
pressure, of a body of elastic fluid acting on the opposite side of said piston, a
continuously operating pump for supplying the elastic fluid, and means controlled
by the position of the piston, to permit the escape of elastic fluid from said body,
and prevent its escape, to secure the proper pressure of the elastic fluid under
changes of liquid pressure, substantially as described.
36. The combination with a piston acted upon by a column of liquid under
pressure, of a body of elastic fluid acting on the opposite side of said piston, a
continuously-operating pump for supplying the elastic fluid, and means actuated
on the movement of the piston against the pressure of the liquid, to permit the
escape of elastic fluid from said body, and, on the movement of the piston in the
opposite direction, to prevent the escape of elastic fluid, substantially as described.
37. The combination with a piston acted upon by a column of liquid under
pressure, of a body of elastic fluid acting on the opposite side of said piston,
means actuated on the movement of the piston against the pressure of the liquid,
to permit the escape of elastic fluid from said body up to a certain point of travel
of said piston, and means for permitting a large escape of said elastic fluid from
said body upon the further movement of the said piston, substantially as
described.
38. The combination with a piston acted upon by a column of fluid under
pressure, of a body of elastic fluid acting upon the opposite side of said piston,
a pipe connecting said cylinder with an elastic fluid supply, and arranged inside.
the end of the cylinder, so as to be closed by the piston before the latter reaches
the end of the cylinder, and a normally-open small connection between the
cylinder and elastic fluid supply, through which elastic fluid is admitted when
the main connection is closed, substantially as described.
39. The combination with a column of liquid, under pressure, of a piston
subjected to the pressure of the column of liquid, a second piston opposing the
movement of the first mentioned piston by said liquid, and a body of elastic fluid
between said pistons, for relieving variations in pressure of the column of liquid,
substantially as described.
40. The combination with the force main of a pumping engine, of a piston
subjected to the pressure of the force main, a second piston opposing the move-
ment of the first mentioned piston by said liquid, and a body of elastic fluid
between said pistons for relieving variations in force main pressure, substantially
as described.
41. The combination with a cylinder having a valve controlling the admission
and cut-off of the motor fluid, and a separate exhaust valve, of a rocker provided
with a block connected to the valve controlling the admission and cut-off; and

page_text: adjustable to vary the point of connection between the valve connections and
rocker, means for actuating said first-mentioned valve for admission and cut-off
through said rocker, and means independent of the adjustment of said block,
for actuating said exhaust valve, substantially as described.
42. The combination with cylinder A, having single valves controlling the
admission and cut-off of the motor fluid, of rocker c having adjustable connection
blocks 3, links connecting said blocks to the respective valves, and means for
actuating said rocker c, for operating the valves for admission and cut-off through
said rocker c, substantially as described.
43. The combination with a cylinder having single valves controlling the
admission and cut-off of the motor fluid at opposite ends of the cylinder, of
rocker e mounted between said valves, link connections between said rocker and
the respective valves, and rocker on which rocker is pivoted at such point
that each of the valves is substantially stationary while the other valve is being
operated by the rocker c for cut-off, substantially as described.
44. The combination with a cylinder having single valves controlling the
admission and cut-off of the motor fluid at opposite ends of the cylinder, of
rocker e, link connections between said rocker and the respective valves, rocker
on which said rocker is pivoted, and by which the valves are operated for
admission, said rockers and link connections being constructed and arranged to
hold each of said valves substantially stationary while the rocker d is actuating
the other valve for admission, substantially as described.
45. The combination with a cylinder and a valve at each end of the cylinder
controlling the admission and cut-off of the motor fluid, of rocker & mounted on
the cylinder, rocker e pivoted on said rocker & between said valves, a link con-
nection between said rocker c and each of said valves, and means for actuating
rockers and d, for operating the valves through locker e, for admission an
cut-off, substantially as described.
46. The combination with a cylinder having a valve at each end of the cylinder
controlling the admission and cut-off of the motor fluid and separate exhaust
valves, of rocker & mounted on the cylinder, connections between said rocker d
and the exhaust valves, rocker e pivoted on said rocker d between the valves, a
link connection between said rocker and each of the valves controlling the
for operating the
admission and cut-off, and means for actuating rockers and
valves through rocker for admission and cut-off and for operating the exhaust
valves through rocker d, substantially as described.
47. The combination with a cylinder and an oscillating valve at each end of
the cylinder controlling the admission and cut-off, and cranks 12 on the valve
stems, of rocker mounted on the cylinder, rocker e mounted on said rocker d,
between the valves, single links, 13, connecting said rocker e to the cranks 12,
and means for actuating said rockers c, d, to operate the valves for admission
and cut-off through said rocker c, substantially as described.
of than 1808
NEWTON & SON,
Agents for the Applicant.