Improvements in Pumping Engines.
Year: 1898

page_text: Date of Application, 26th July, 1898-Accepted, 10th Sept., 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 Pumping 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 :-
The object of the present invention is to provide an improved valve movement
for pumps, whereby a more uniform action of steam and power pumps may be
secured, and the speed at which they can be operated successfully increased; and
the present invention relates particularly to means for applying fluid pressure to
positively close the valves as the plunger reaches the end of its stroke, and controlling
this fluid pressure by a valve mechanism actuated from some moving part of the
pump, so as to apply or cut off the pressure at the proper time to secure the proper
operation of the pump valves.
The fluid pressure thus controlled by the valve mechanism may be applied to the
valves against the pumping pressure, so as to close the valves in the proper manner,
or the pressure controlled by the valve mechanism may be applied against a constant
pressure tending to close the valves, so as to balance or overcome the constant
pressure when the valves are to be opened, or the valve mechanism may control a
fluid pressure so as to apply it alternately above and below the valves, according as
the valves are to be closed or opened. The fluid pressure controlled by the valve
mechanism may be taken from any suitable source, either within or outside of the
pump, and the source may have a constant or varying pressure, but a convenient and
efficient construction, and one which will probably be found preferable in most cases,
is-provided, by using some part of the force side of the pump as the source of pressure,
and actuating the valve mechanisin so as to apply this pressure to the pump valves
for closing them, and to relieve this pressure when the valves are to be opened.
This closing pressure is preferably applied both to the force and suction valves, so
as to ensure the closing of these valves before and behind the plunger at or about
the same time, but the pressure may be applied only to the force valves, and instead
of applying the pressure directly to these valves, it may be applied to an auxiliary
valve or valves controlling communication between the water cylinder and the force
main, so as to secure the results desired, and similar auxiliary valves may be used
also with the suction valves, if desired.
The improved valve movement is applicable generally to different forms of pumps,
whether operated by steam or power, but is of especial value as applied to direct-
acting steam pumps in which the improved valve movement co-operates with other
features of the construction to secure certain special results not obtained in other
pumps.
Thus, with the improved valve movement in which the valves are positively closed
so as to cut off the pressure of the force main in front of the plunger, as the piston
approaches the end of its stroke, the piston and plunger are cushioned by the water

page_text: retained within the pump cylinder, and may be stopped thereby, wholly or partially, thus
doing away with the steam cushion or, if it be retained, avoiding the necessity of
adjusting the cushion in accordance with the speed of the pump, and rendering it
possible to employ only a moderate steam cushion at all speeds. While the piston
and plunger may be stopped entirely by applying this increased pressure upon the
plunger at the end of the stroke, it is preferred to use a moderate amount of cushion in
the steam cylinder in connection therewith, in order to divide up the stopping force,
and because the cushion is desirable in order to fill up the clearance spaces in the
steam cylinder.
With the improved valve movement also, and the high speed rendered possible
thereby, it will be found that the steam may be cut off earlier in the stroke than in
the ordinary direct acting pumps now in use, and a higher economy of steam obtained
thereby, as the momentum acquired by the piston and plunger at the high piston
speed will be sufficient to carry them to the end of their stroke, without the steam
following as late in the stroke as with lower speeds.
The invention is applicable either to single or duplex pumps, but secures many
special advantages in duplex pumps, the most important of which is, that prevents
the recoil of the plungers and pistons which otherwise would take place at the ends
of the strokes when running at very high speeds, and avoids the injurious effects
resulting from the action of the recoil of the plunger on one side of the pump, thus
making practicable speeds that have heretofore been unattainable in duplex pumps
with the uniformity and smoothness of action desirable.
The invention will now be described as applied to a duplex direct-acting pump of
the preferred form, and a modification thereof, and to pumps of other classes.
In the drawings:-
Fig. 1 is a side elevation of a triple expansion "Worthington" duplex pump
provided with the improved valve movement.
Fig. 2 is a plan view of the same.
Fig. 3 is a longitudinal section, taken centrally through the suction valves of the
water end on the line 3 of Fig. 2.
Fig. 4 is a central longitudinal section through the force valves and pump
cylinder on the opposite side of the pump on the line 4 of Fig. 2.
Fig. 5 is a vertical cross section, taken centrally through the pump valves, on the
line 5 of Figure 2.
Fig. 6 is a vertical cross section of the valve mechanism on the line 6 of Figure 8.
Fig. 7 is a horizontal section on the line 7 of Fig. 8.
Figs. 8 and 9 are vertical sections on respectively the lines 8, 9, of Fig. 7, partially
broken away to show the ports, and showing the valve in different positions.
Fig. 10 is a longitudinal section taken centrally through the steam and water
cylinders, on one side of a duplex pump, of a modified construction employing
auxiliary pump valves on the force side.
Fig. 11 is a plan view of the same.
Figs. 12 to 15 show double-acting pumps of a well-known class, with piston valves
controlling the fluid pressure, and embodying certain specific features of the in-
vention.
Fig. 12 is a vertical. longitudinal section of a pump, with one form of valve
mechanism.
Figs. 13 and 14 are detail sectional views of a balanced slide valve shown in
Fig. 12.
Fig. 15 shows a pump provided with a modified form of piston valve mechanism.
Figs. 16 to 20 illustrates the invention as applied to crank pumps of different
classes.
Fig. 16 is a diagrammatic view illustrating the principle of the valve closing
devices, disconnected from the rest of the pump.
Fig. 17 is a vertical sectional elevation showing the invention applied to the
cylinder of a pump of the class having a single acting suction and double acting
delivery.

page_text: Fig. 18 is a horizontal section of the same on the line 18 of Figure 17.
Fig. 19 is a vertical section, showing the invention applied to the suction and
delivery valves of a vertical single-acting plunger pump; and
Fig. 20 is a view, partly in vertical section, and partly in elevation, showing the
invention applied to a double-acting outside plunger pump.
Referring now particularly to Figs. 1 to 9, the engine shown is, as to its general
construction, a Worthington duplex direct-acting triple-expansion pump, having the
high intermediate and low pressure cylinders A, B, C, and A, B, C, on opposite
sides arranged in line, with the high pressure cylinder inside, and having the two
water cylinders D, D¹ on the opposite sides of the pump, the plungers d, d¹ on oppo-
site sides of the pump being connected by the plunger rods e, e¹, to cross heads f. f¹
connected to the steam pistons, the low pressure pistons being connected to the cross
heads by rods passing outside the intermediate and high pressure cylinders, and the
intermediate pressure piston being connected to the low pressure piston.
Steam supplied to the high pressure cylinders through the induction pipe E, the
exhaust passing from the high pressure to the intermediate pressure cylinder through
the pipe F, and from the intermediate to the low through the pipe G, and the low
pressure exhaust through the exhaust pipe H to the suction main, as shown. The
induction steam valves are actuated from the cross-over valve motion g through the
connecting rods 10, connected to the valves h by the usual crank arın connection, a
single oscillating valve being shown as used for each cylinder, and the cut-off valve i,
which are shown as used only on the high-pressure cylinders, are actuated from the
cross-over motion g by the connecting rods 11.
The steam cylinders will preferably be constructed, as usual, with separate induction
and exhaust ports, so that the pistons, when near the end of their stroke in either
direction, cover the exhaust ports, and confine a small amount of exhaust steam in
front of the ends of the cylinders, by which the pistons are cushioned and arrested.
This is a common method of cushioning, but it will be understood that any other
form of apparatus may be used for this purpose, and that, as above stated, all
cushioning of the steam pistons may be omitted, and the pistons and plungers stopped
by water pressure only.
The water cylinders are provided with the usual force valves m, n, m¹ n¹, and
suction valves o, p, o¹, p', the force valves m, n, and suction valves o, p, communicating
respectively with the water cylinder D, at the end next to, and farthest from, the
steam end, and the force valves m¹, n', and suction valves o¹, p¹ corresponding thereto,
on the opposite side of the pump on cylinder D¹, these force and suction valves
working in and controlling respectively the force and suction chambers K, K¹
and L, L on opposite sides of the pump, and are connected in turn with the force
main M and suction main N, the usual air chamber O being shown on the force
main.
In the operation of duplex pumps of this class, the pistons move in opposite
directions during a part of the stroke, and in the same direction during the rest of the
stroke. When moving in the same direction, the same plunger is always in advance,
in whichever direction the two plungers are moving, and in accordance with
established practice, the terms "leading" and "following" will be used herein to
refer respectively to the sides of the pump, the plungers of which lead or follow, when
both are moving in the same direction. In the pump shown, the cylinder D is
on the leading side, and the cylinder D¹ on the following side of the engine.
All the parts thus far described may be of any other usual or suitable construction,
the construction shown being selected simply as the most desirable type of duplex
direct-acting pumping engine for the embodiment of this invention.
The parts in which the invention is embodied in its preferred form, as applied
to this pump, will now be described. Each of the force valves m, n, m¹, n¹ is
connected to the piston rod 1, of a piston 2, these pistons moving in small motor
cylinders 12, 13 and 14, 15, mounted above the respective force chambers on opposite
sides of the pump. The suction valves o, p, o¹, p¹ are similarly connected by the

page_text: '
piston rods 3 to pistons 4 moving in cylinders 16, 17, and 18, 19, mounted above
the respective suction chambers on opposite sides of the pump.
Each of these small cylinders is entered, at its upper end, above the piston, by a pipe
through which fluid is transmitted to the cylinder, so as to exert the required
pressure upon the piston for closing the valve, and the pipes leading to the different
cylinders are controlled by a valve mechanism on each side of the pump operated
from a moving part of the latter, the pressure for the cylinders being supplied to the
valve mechanism from the force main or other suitable source of pressure, preferably
within the pump, although it is obvious that this pressure may be drawn from the
outside, if, for any reason, it be found desirable. In the construction shown, the
connections and valve mechanism are as follows:-
The cylinders 12, 13, controlling the force valves m, n, and the cylinders 16, 17,
controlling the suction valves o, p, on the leading side of the pump, are connected
to the valve mechanism V respectively by pipes 20, 21, and 22, 23, and the
cylinders 14, 15, controlling the force valves m¹, n¹, and the cylinders 18, 19,
controlling the suction valves o¹; pl, on the following side of the pump, are connected
to the valve mechanism V₁ respectively by the pipes 24, 25, and 26, 27, and the
valve mechanisms V, V₁ on the opposite sides of the pump are connected with the
force main by the pipes 28, entering at the top, and each of the valve
mechanisms V, V₁ is provided with an exhaust pipe 29 connecting the valve chamber
with the suction main or other receiver for the exhaust.
The valve mechanism controlling these pipes, shown in detail in Figs. 6 to 9,
comprises a valve chamber 8, with which the exhaust pipe 29 communicates
directly, and which has, upon the opposite side from the exhaust pipe, two cross-
over ports 6, 7, forming the connection between the port 5 of the pipe 28 from
the force main and the pipes to the respective cylinders above the pistons
connected to the force and suction valves, or the connections between these pipes
and the valve chambers on the exhaust side of the valve t.
In the valve mechanism shown in detail, which is the valve mechanism V₁ on the
following side of the pump, the pipes 24, 27, to the cylinders 14, 19, controlling
respectively the force valve m¹, and the suction valve p¹, are connected by the port 6,
and the pipes 25, 26, to the cylinders 15, 18, controlling respectively the valve n¹, and
suction valve o¹, are connected by the port 7, these ports 6, 7, thus forming, with the
connecting pipes 24, 27, and 25, 26, pressure chambers, each controlling a suction and
a delivery valve. The valve t, therefore, in the position shown in Fig. 8, will open
pipes 24, 27, and cylinders 14, 19, to pipes 28, through ports 5, 6, so as to apply the
force pressure to valves m¹, p¹, and will open pipes 25, 26, to the exhaust pipe 29,
through port 7 and valve chamber on the exhaust side of the valve t, while the shifting
of the valvet from the position shown in Fig. 8 to that shown in Fig. 9, will reverse
these connections. This supplemental valve t, therefore, alternately admits fluid from
the force main to, and discharges it or permits its discharge to the suction main
from, each of the pressure chambers in turn, so as to properly apply and release the
closing pressure on the valves controlled by the respective pressure chambers, to
secure the desired results.
As the plunger d¹ reaches the end of its stroke from right to left, therefore, the
valve t is in the position shown in Fig. 8, and the force valve m¹ and suction valve p¹³,
respectively in front of and behind the plunger, closed by the force pressure from
pipe 28, and the cylinders controlling the force valve n¹, and suction valve o¹, opened
to the exhaust pipe 29, so as to permit these valves to open when the plunger is
reversed for the next stroke, while, as the plunger d¹ reaches the end of its stroke from
left to right, the valve t is in the position shown in Fig. 9, and the force valve n¹ and
suction valve o¹, respectively in front of and behind the plunger, are closed by the
force pressure, and the cylinders controlling force value m¹ and suction valve p¹ are
opened to the exhaust pipe 29.
The valve mechanism V on the leading side of the pump is exactly the same, and
controls the pipe 20, 21, and 22, 23 to the cylinders 12, 13, and 16, 17, in the same

page_text: The oscillating valves on the opposite sides of the pump are actuated by the
following means:—
The valve stem 30 is provided with a crank arm 31, which is connected by a rod 32
with a crank arm 33 on a rock shaft extending across the cylinder, and from a crank
arm on the inner end of which a connecting rod 34 runs to the levers 35 of the valve
motions g, so that these valves are shifted in proper time by the movement of the
piston rods, to vary the pressure as required.
The operation of the mechanism described is as follows:-
In order to make the operation clear, the general action of duplex pumps of the
class shown must be kept in mind, which is as follows:-
As the piston and plunger on the leading side move to the right, the water in front
of the plunger d on that side will be forced past the force valve n in front of the
plunger, raising the valve in the usual manner, and at the same time the water will
be drawn in, raising the suction valve o behind the plunger. As the piston and
plunger on the leading side approach the end of their stroke, the cut-off valves will
operate to cut off the steam behind the piston, and the latter will cover the steam
exhaust port and cushion itself upon the steam confined in the steam cylinder beyond
this port, as usual in such constructions, and the piston and plunger will thus be
arrested. When the piston on the leading side of the pump is on the latter part of
its stroke, the exact point varying in different pumps, and being adjusted in the
same pump in accordance with the duty to be performed, the piston and plunger on
the following side of the pump will have completed the stroke in the opposite direc-
tion, the cut-off valves operating and the piston being cushioned as just described in
connection with the leading side, & the piston and plunger will start in the same
direction as that in which the piston and plunger on the leading side are then mov-
ing, that is, from left to right, the two pistons and plungers moving in the same
direction until the piston and plunger upon the leading side have completed the
stroke, when the motion of the latter is reversed, and they return, partially during
the forward stroke on the following side, and thus the operation continues.
This is
the usual operation in duplex pumps.
As shown in the drawings, the plunger d on the leading side of the pump has just
been reversed, and is commencing its stroke from right to left, while the plunger d¹
on the following side of the pump is still moving froin left to right, being about one-
half stroke. In this position of parts, the force valve m and suction valve p on the
leading side of the pump are open, and the force valve n and suction valve o on the
same side of the pump closed, while on the following side of the pump the force valve
n and suction valve o¹ are open, and the force valve m' and suction valve p₁ closed,
and the operation of the invention will be understood as starting at this point.
As the plungers continue their movement, and the piston and plunger on the
following side of the pump approach the end of the stroke, the cut-off valve i on the
following side of the pump will be actuated from the piston rod on the same side, to
cut off the steam behind the piston, as usual in such constructions, and the valve
mechanism V on the following side of the pump will be actuated from the leading
side of the pump through the valve movement g, and the connections previously
described, so as to shift the valve within the valve chamber a into the position
shown in Fig. 9, and admit the force pressure from the pipe 28 through pipes 25, 26
to the motor cylinders 15, 18, above the pistons 2, 4, which control respectively the
force valve n¹ and suction valve o' on the following side of the pump, respectively in
front of and behind the plunger, and by this pressure these valves are gradually and
positively closed just as the plunger on the following side reaches the end of its
stroke from left to right.
As the piston and plunger d on the leading side of the pump continue their stroke
from right to left, however, the main steam valves h on the following side of the
pump are shifted through the valve motion g and connections, as usual in this class
of duplex pumps, and the piston and plunger on the following side of the pump then
move from right to left in the same direction as the piston and plunger on the
leading side of the pump, the pipes 24, 27, controlling the force valve m¹ and suction

page_text: valve p¹, respectively in front of and behind the plunger, as it is reversed, being
opened to the exhaust pipe 29, as shown in Fig. 8, so that these valves may be
opened by the water current.
As the plunger d on the leading side of the pump approaches the end of its stroke,
the cut-off valves on the leading side are actuated from the sare side of the pump,
and the valve mechanism V on the leading side of the pump, actuated from the
following side, as already described in connection with the latter, so as to apply the
force pressure from pipe 28 to the pistons 2, 4, in the cylinders 12, 17, controlling
the force valve m and suction valve p, respectively in front of and behind the plunger,
so as to close these valves gradually and positively, as the plunger on the leading
side reaches the end of its stroke from right to left, opening the cylinders 13, 16,
controlling the force valves n and suction valve o, to the exhaust pipe 29, so as to
permit the opening of these valves by the water current, as the piston and plunger
are reversed.
The main valves k on the leading side of the pump are then reversed by the
following side, as the piston and plunger on the following side continue their stroke
from right to left, and thus the operation is constantly repeated during the action of
the pump.
The time of closing of the valves may be adjusted by proper construction of the
pump, as by proportioning the size of the pipes and motor cylinders. It will, how-
ever, be found convenient, and may in some cases be necessary, to provide means
whereby the passage of the water through the pipes may be adjusted, or the operation
of the pistons and valves otherwise controlled so that the valves shall be fully closed,
just as the plunger reaches the end of its stroke. This may be conveniently done by
means of the throttle valves 9 upon the pipes by which the pressure is transmitted, the
passage of the water, and consequently the variations of the pressure above the motor
pistons, being thus adjusted as desired. Any other suitable means for adjusting the
time or rapidity of movement of the valves may be used.
While the construction thus far described embodies the invention in its preferred
form for large engines, it will be understood that the invention inay be applied in
constructions of widely different forms. Thus, in the organization above described,
the force and suction valves are operated directly by the fluid pressure, but it will be
understood that the valves thus operated may be either the main force and suction
valves, as ordinarily applied and as above described, or auxiliary valves located any-
where in the force and suction chambers of the water cylinders, either between the
main valves and force and suction mains, or between the plunger and main valves.
In Figures 10 and 11, there is shown a simple organization embodying the broad
features of the invention, in which the fluid pressure is used for controlling the
valves on only the force side of the pump, and is applied to auxiliary valves
located between the force valves and force main, and operating to close com-
munication between the water cylinders and force main, and cut off the pressure
in front of the plunger, as the latter reaches the end of its stroke, as before described.
The pump shown is, in general construction, a simple duplex pump of substantially
the same character as that previously described, and having the steain cylinders A, A¹,
water cylinders D, D¹, plungers d d and piston rods e el on respectively the leading
and following sides of the pump. The steam cylinders have the usual valve movement
g, as in the pump previously described, and by which the main slide valve k on each
side is actuate from the other side through the valve rods 50, as usual in duplex
engines of this class.
The steam cylinders are preferably provided with separate induction and exhaust
ports x, y, so that as the steam pistons S, near the end of their stroke in either
direction, they cover the exhaust port y, and confine a small amount of exhaust steam
in front of them in the cylinder, by which the pistons are cushioned. This is a
common method of cushioning, but it will be understood that any other form of
apparatus may be used for this purpose, and, as stated above, all cushioning of the
steam pistons may be omitted, and the pistons and plungers be stopped by water pressure

page_text: only. The induction ports are controlled by cut-off valves operating to cut off
the steam as above described. The construction of rotary cut-off valves is that
shown in Patent No. 2342 of 1884 and the operating connections are substantially
the same, and need not be particularly described herein, the cranks 100 on the valve
stems being connected to lever 101, which is operated from the valve movement by
connecting rods. 102, as shown. It will be understood, however, that any other
form of cut-off valves and operating connections may be substituted, if desired.
In this construction, the means for controlling the auxiliary valves are as follows:-
a cylinder 36 is used on each side of the pump, in which moves a piston 37, having
its rods 38 connected to a double-disk valve u, which closes one or the other of
the ports leading from the force chamber to the force inain, according to the position
of the piston 37. This cylinder 36 is provided with a valve chamber v, in which moves
an oscillating valve w controlling ports connecting the opposite ends of the cylinder 36
with the valve chamber or an exhaust cove, so as to be controlled by the valve for
connection either with a pipe 39 from the force main to the valve chamber, or an
exhaust pipe 40 from the exhaust cove, and shown as connecting with the suction
main. The valves ware operated by common crank arms with connecting rods 41
to the levers 42 of the valve motion. In the construction shown, the valves ware
actuated from the opposite sides of the pump, but it will be understood that in
this construction, also, as in the construction previously described, the valve on each
side may be operated by the piston rod on its own side, instead of by that on the
opposite side.
It is evident that the operation of this construction is substantially the same as
that previously described, the movements of the piston rods shifting the valves w
through the rods 41, so as to actuate the valves u to open the port leading from the
force chamber to the force main at one end of the cylinder, and close the port leading
from the force chamber to the force main at the other end of the cylinder, as the
plunger reaches the end of its stroke, the piston 37 being actuated in one direction or
the other by the difference between the force and suction pressures upon its opposite
sides.
While, in the constructions shown, the fluid pressure closing the valves is controlled
by the action of the pump, so as to apply or relieve it, as required, it is evident that
a construction may readily be devised and substituted therefor, in which a constant
pressure is employed above the pistons, and the pressure controlled by the action of
the pump
is admitted below the pistons, this requiring only a reversal of the action of
the valve mechanism, so as to apply the pressure to counter-balance the pressure
above the pistons, when the valves are to be opened, and to relieve the pressure below
the pistons, so as to allow the pressure above the pistons to close the valves at the
proper time.
By the use of an auxiliary valve placed. between the cylinder and main, either
between the plunger and valves, or between the valves and main, the function of
the valves is not altered in any respect. In case the auxiliary valve becomes
obstructed at any time, or held from its seat by any foreign matter passing
through the pump, the force valves are still free to act, and prevent the pressure of
the main from entering the water cylinder during the suction stroke. Further,
in case of any accident, either to the auxiliary valves, or to the controlling connections,
the auxiliary valve may be removed for repair, during which interval the pump may
operated, as in the common construction, at a somewhat slower speed than is
customary with the auxiliary valve in commission.
Referring now to the construction shown in Figures 12 to 15, A2 indicates the pump
barrel, B' the suction chamber, and C² the pressure chamber, from which a stand pipe D²
rises. A cylinder E' is connected with said pressure chamber C² by a pipe F2, extending
from the upper portion of said cylinder E2 to the side of said pressure chamber (2.
The plunger G2, which is connected at one end with the piston rod H2 of a Corliss
engine passes through said cylinder E² into said pump barrel A2, and is enlarged at
its forward end to twice the cross sectional area at its rear end portion, so that

page_text: when moving toward the forward limit of its movement, one-half the amount of
water forced into said pressure chamber C² thereby, will pass through said pipe F2
into said cylinder E2, and, upon its return stroke, said enlarged portion of said
plunger will force the water out of said cylinder E2 into said pressure chamber C²,
thus making a very simple double-acting pump.
A valve seat 104 is mounted between said suction chamber B2 and said pump
barrel A2, upon which the induction valve 105 is seated. Said induction valve 105
is mounted upon a valve stemn 106, which carries two differential pistons 107 and
107". Said piston 107 is the larger, and uppermost, and moves in a cylinder 108
(see Fig. 15) on the head 109 of said pump barrel A. Said piston 107, which may
be termed the endmost piston, is so constructed that the area of its upper face is
greater than the area of its lower face, and that its lower face is of greater area
than the upper face of the piston 107, which may be termed the innermost piston.
Said piston 107 moves in a passage 108ª extending between said cylinder 108 and
said pump barrel A2 and the lower face thereof, which is acted upon by the pressure
in said pump barrel, may be of the same or smaller area than said valve seat 104.,
The said piston 107 is actuated by fluid pressure from the stand pipe D2 as herein-
after more fully described.
Said valve seat 104 consists of a cylindrical body portion 110, provided with an
interiorly extending flange 111 at its upper end, the upper face of which is turned to
form the valve seat. A hub 112 is mounted in the centre of said valve seat 104,
between the spokes 113, and is adapted to receive an extension of said valve stem 106
below said valve 105 to centre the same. A collar 114 on said valve stem, below said
head 109, is adapted to limit the upward movement of said induction valve 105.
Said pressure chamber C2 is provided, at its inlet end, with a valve seat 115, of the
same construction as said valve seat 104, upon which the eduction valve 116 is
mounted. Said valve 116 is mounted upon the valve stem 117, carrying two
differential pistons 118, 118ª. Said piston 118 is the larger and uppermost, and
moves in a cylinder 119 on the head 120 of the pressure chamber C2². The area of the
upper face of said piston 118 is also greater than the area of the lower face of said
piston 118, which is acted upon by the pressure in the pressure chamber of the pump,
so that upon bringing equal pressure upon the said upper face of said piston 118, said.
valve 116 will be moved against the action of the pressure upon said lower face of said
piston 118ª. Said piston 118 moves in the passage 119 between said cylinder 119
and the pressure chamber. The lower face of said piston 118ª is preferably of smaller
or equal area with said valve seat 115. In the drawings the areas of the lower faces
of the piston 107* and 118* are shown as less than the areas of the respective valve
seats. Said valve stem 116 is also provided with a collar 114 to limit its upward
movement.
A balanced slide valve 121 is mounted-upon said pump adjacent to said pressure
chamber, and is preferably secured thereto. Said slide valve 121 consists of a
cylinder 122, in which a piston rod 123 (see Fig. 14), carrying pistons 124, 125, 126,
and 127, moves. Said piston rod 123 is connected with the arm 128 of a bell-crank
lever 129 pivotally mounted upon an arm 130 on said head 120, by means of a
connecting rod 131. The other arm 132 of said bell-crank lever 129 is connected
with the valve gear of the Corliss engine by means of a rod 133, represented by a
dotted line in the drawings.
A pipe 134 is connected with said valve 121 near its upper end, and connects the
same with said suction chamber B. A pipe 135 connects said valve with the head 136
of said cylinder 119. A pipe 137 connects the same with the lower end of the
cylinder 108, and a pipe 138 with the head of said cylinder 108. A pipe 139
connects said pipe 137 with the stand pipe D². A pipe 140 connects the lower end
of said valve with the suction chamber B2. Valves are provided in all of said pipes for
obvious reasons.
The operation of this valve gear, as shown in Figs. 12, 13, and 14, is as follows:-
In Figure 12, the plunger G2 is shown at the forward limit of its movement, and
said piston rod 123 and pistons 124, 125, 126, and 127, at the upper limit of their

page_text: movement. Said plunger is about to begin its return stroke, and at this time the
pressure in the pump barrel A2 and pressure chamber C2 is equal, and consequently
the pressure on both sides of the eduction valve 116 is balanced. The pipes 135
and 137 are in communication with each other through said valve 121, and water
under pressure is supplied thereto from the stand pipe D2 through the pipe 139, and
flows therethrough into the cylinders 108, and 109, whereby said piston 107 is forced
upwardly to open said valve 105, and piston 118 forced downwardly to close valve 116.
The pipe 138 is, at this time, in communication with said pipe 140, thus connecting
the upper chamber of said cylinder 108 with said suction chamber B2, to permit the
escape of the water in said upper chamber of said cylinder 108. An opening is
provided in the lower end of said cylinder 119, to permit the passage of air to and
from the same, in accordance with the movements of said piston 118.
As said plunger G² reaches the rearward limit of its movement, the said slide valve
is in the position shown in Figure 14, and so connects the pipes as to reverse the
position of the valves 105 and 116. In this position, the pipe 135 communicates
with the pipe 134, to allow the water in the cylinder 119 to escape to the suction
chamber, when the valve 116 is relieved, or partly relieved, from the pressure in said
pressure chamber C2, and is forced upwardly by the excessive pressure in the pump
barrel. At the beginning of the forward stroke of the plunger G², and just previous
to the opening of the valve 116, the pressure upon the upper face of said valve
exceeds the pressure upon the lower face thereof, by the area of the valve seat, and
to relieve or partially relieve said valve from the excess of pressure, for the purpose of
causing it to open more quickly, the piston 118 is provided, the lower face of which
has an area, as above stated, either equal to, or less than, said valve seat. Obviously
the pressure against the same will counteract, or partially counteract, the excessive
pressure upon the upper face of said valve 116, due to the area of the lower face being
lessened by the area of the valve seat, and thus cause said valve to open more promptly
than it otherwise would.
The piston 107ª performs the same office for the valve 105. The pressure in the
lower chamber of the cylinder 108 is constant; and pressure is admitted into the
upper chamber through pipes 137 and 139, while the upper face of the piston 107 is
released from pressure, owing to the communication established between said pipes
138, 139, and 140, by the said position of the valve 121. Owing to the greater area
of the upper face of said piston 107, the pressure on the same will overbalance the
pressure in said lower chamber, and force said piston downwardly, to close said valve
105. Obviously, the pressure in the pump barrel A² must exceed the pressure in
said pressure chamber C2, when said valve 116 is opened.
Fig. 15 is a modified form of construction of this valve gear, the action of which is
the same, though accomplished in a different manner. In this construction, balanced
slide valves 142 and 143 are mounted upon the head of the cylinders 108 and 119
respectively (see Fig. 12). Pipes 144, and 145 connect said slide valves 142 and
143 respectively with said stand pipe D². A pipe 146 connects said pipe 144 with
the lower chamber of said cylinder 108, thus keeping constant pressure in said
chamber. A pipe 147, connecting with both said valves 142 and 143, connects the
same with the suction chamber B². The plungers of said valves 142, 143, are
connected with the end of an arm 148, which is pivoted at its middle portion to an
arm 149 of said pressure chamber C2. In this construction, the valve stem 117 is
shown as provided with only one piston 118 (see Fig. 12). The cylinder 119, in
which the same moves, opens full into the pressure chamber C2, the lower face of
said piston being reduced in size by the cross sectional area of the valve stem 117.
In the positions shown in said Fig. 15, the upper end of said cylinder 108 would
be in comminunication with said pipe 147, to permit the escape of the water therefrom,
as said piston 107 is forced upwardly by the pressure in the lower chamber of said
cylinder 108. The cylinder 119 is in communication with the pipe 145, thus
As said
admitting pressure thereto, and forcing said valve 116 down upon its seat.
plunger G2 reaches the opposite limit of its movement, said cylinder 119 will com-
municate with said pipe 147, and. the upper chamber of said cylinder 108 will

page_text: communicate with pipe 144, thus admitting pressure thereto, and causing said
valve 105 to be forced upon its seat.
One end of said arm 148 of said bell-crank lever 129 may obviously be connected
with any moving portion of the Corliss engine driving said pump, or may be operated
by mechanism connected with the plunger of said pump. In Fig. 15 said arm 148
is connected with the upper end of an arm 150 rigidly mounted upon a rock shaft 151
mounted in bearings in uprights on the bed of said pump. An arm 153 is rigidly
mounted, at its middle portion, upon said rock shaft 151 and extends slightly
upwardly at both ends. Said arm 153 is provided at its ends with adjustable shoes
154, having inclined upper faces adapted to be engaged by an anti-friction roller 155,
mounted upon the projecting end of said plunger G². Said shoes 154 are provided
with downwardly extending flanges 156, through which adjusting screws 157 pass
into said arms 153. Obviously, any other suitable adjusting device could be
employed. During the movement of said plunger G2, said anti-friction roller 155
will alternately engage each of said shoes 154, and depress the same, thereby
operating said rock shaft 151, and causing said arm 150 to swing to and fro, thus
obviously operating said valves 142 and 143. The construction could also be applied
to the construction shown in Fig. 12.
The action of the devices shown in Figs. 12 to 15 for operating the valves, is very
efficient, inasmuch as it is quick, and occurs only at the end of each stroke, thus
holding said valves in proper position for the full period of the stroke, and quickly
changing their positions at the end thereof. The action is also positive, and exceed-
ingly simple, so that repairs are seldom necessary.
Referring now to the construction shown in Figures 16 to 20, the principle of
operation of the device, in these constructions, may be explained with the aid of the
diagram of Figure 16, in which A³ indicates a pump valve, arranged so as to be
opened in the usual way by the pressure of the fluid underneath it compressing the
light spring a³. The upper end of the valve stem g³ is connected to a flexible
diaphragm, m³, which forms one side of the chamber B³. This chamber, which is
called the pressure chamber, connected by the passage D³ with the valve chest t³,
containing a valve, C³. From the valve chest t³, the passage F³ leads to any conve-
nient source of fluid under pressure, such as a steam boiler, compressed air reservoir,
head of water, or the like. The passage E³ leads to the atmosphere, or to some body
of fluid under lower pressure. The valve C³ is operated by some suitable connection
with the mechanism of the pump; and, according as it is moved to the left or right
from its middle position, puts the port D³, leading to the pressure chamber, in com-
munication with the passage E3 or with the passage F³. Thus, the pressure applied
to the diaphragm m³, and by it to the pump valve A³, is varied by the operation of
the valve C³,
The mechanism is shown in Figure 16 in such a position that the chamber B³ is in
communication with the port E³, and the pressure on the diaphragm is such as to
permit the fluid driven by the pump piston to lift the valve A³ from its seat, and to
flow through the port in the direction of the arrow. Now, if the motion of the pump
piston were to be suddenly reversed, the valve C³ remaining in the position shown,
a momentary reversed flow of fluid downward past the valve A³ would result before
the spring a would have time to close it, and the valve would be driven to its seat
with a violence depending upon the pressure of the fluid pumped, and the rapidity of
reversal of the piston's motion. To forestall this action, the valve C³ is moved towards
the right, just previous to the reversal of the motion of the pump piston, so as to
admit the fluid pressure from F3 through the passage D³ to the chamber B³. This
pressure, acting on the valve A³, forces it quietly to its seat against the gradually
diminishing flow of fluid upward through the port, so that when the reverse motion
of the piston begins, the valve is already closed. Before the time for again opening
the pump valve A³ arrives, the valve C³ has moved back, so as to connect the pressure
chamber B3 with the exhaust passage E3, thus relieving the pressure on the valve A³,
and allowing it to be opened easily by the fluid, as soon as the motion of the piston
is again reversed.

page_text: In this construction, the speed of the closing movement of the valve A³ is limited
by the rapidity with which the flaid can enter the chamber B³, and this can be
regulated by a throttle valve in the passage F³, or by adjusting the extent of opening
of the valve C3. The time when the closing movement begins, is conditioned upon
the time of movement of the valve C³, and may be controlled by adjusting the eccen-
tric or other device by which that valve is driven. The force applied to close the
valve A3 depends upon the pressure of the fluid admitted to the pressure chamber B³,
and the area of the diaphragm or equivalent device upon which the pressure acts;
and, by using suitable proportions, any required force may be obtained. All the
elements affecting the closing of the pump valve are therefore under control, and, by
adjustments readily made, any desired closing movement inay be produced.
Of course, the diaphragm m³ is not an essential feature of the construction, and a
piston or equivalent device may be substituted for it; or, by properly enclosing the
back of the pump valve A³, the fluid pressure in the chamber B3 may be made to act
directly on the valve itself.
Figures 17 and 18 show a suction valve A³, and a delivery valve A4, both controlled by
the same valve Cs and pressure chamber B³. 83 indicates the suction pipe con-
nection 3 a passage in communication with the main chambers of the pump cylin-
der, and h³ the connection to the delivery pipe. The latter connects also to the cham-
ber of the pump cylinder, which has no valves. The cross section of the plunger p¹
is made of about one half the area of the main plunger p³, in order to give, on the
delivery side, the effect of a double acting pump. Both pump valves have their
stems g³ and g, extended into the pressure chamber B3, through cylindrical openings
in which they fit loosely, so as to slide freely in and out when the valves move; and the
latter are further guided by the radial plates z³ fitting the side of the port openings.
It is preferred generally to make the valves without closing springs, as shown, so
that they may oppose as little resistance as possible to the flow of the fluid, their
lifting movements being limited by elastic buffers, 3 and 4. It is generally most
convenient also to employ the fluid which is being pumped as the working fluid for
applying the necessary closing force to the pump valves, and accordingly the
admission and exhaust passages F3 and E3 are led from the supplemental valve
chamber t3 respectively to the delivery pipe h³, and the suction pipe 83. The
passage D², as before, connects the valve chainber 13 with the pressure chamber B³.
The action of the supplemental valve C³ in Figure 17, is the same as in Figure 16,
except that, in Figure 17, this valve is of the rotary, instead of the flat slide-valve
type. It is actuated by the rocking lever n³, which derives its motion in any suitable
way from the pump mechanism.
One of the advantages of the construction shown in Figures 17 and 18 is that, by
this method, the valves and pipe connections are all included in a single cylindrical
casing ³, and these may be manufactured and fitted up independent of the pumps to
which they are to be applied, the same valve chest being applicable to a great variety
of pump cylinders. The latter have then simply to be provided with a flanged
connection q³ on the side, or in some convenient place for bolting on the valve chest,
as shown. The delivery valve may be lifted out of the casing when the cover it is
removed; and, by removing the cover ³, access may be had to the suction valve,
which may be taken out also, after being detached from its stem g³.
Figure 19 is a vertical sectional elevation of a single-acting pump, whose
plunger p³ is driven by means of the crank w³, the double beam y³, and the connecting
links 3 and 4. The rocking lever n³, by which the valve C³ is actuated, is connected
by the rod 3 directly to the main crank pin 03. The time and extent of the opening
of the valve C3 may be adjusted by means of the movable pin and the slot in the
lever n³, or by shifting the angular position of the latter on the valve spindle.
Suppose the rotation of the crank to take place in the direction indicated by the
arrow, so that the plunger p³ in the position shown is moving downward, and forcing
the fluid out of the pump cylinder 3 through the annular passage u³ and the delivery
valve A, the suction valve A³ being closed. The valve C3 is in its middle position,
covering the port D³; and, as the sinall plungers formed by the valve steins g³ and g¹.

page_text: are not tight-fitting, the fluid pressure in the chamber B³ is now about the same as
that in the pump cylinder k³. As the plunger p³ approaches the end of its downward
stroke, the rocking lever n³ is moved downward, and the valve C³ is rotated into a
position which puts the port D³ in communication with the port E³. The fluid in
the chamber B³ can now escape into the suction pipe, and the pressure in B³ is
reduced to the suction pressure, so that the superior pressure on the top of the
delivery valve A4 forces it to its seat. If the adjustments are properly made, when
the plunger p³ begins its upward stroke, the delivery valve A4 will be closed.
The pressure chamber B3 being then in communication with the suction pipe, the
suction valve A³ experiences no resistance to opening. As the plunger på nears the
top of its up-stroke, the valve C³ connects the chamber B3 with the delivery pipe h³,
and the fluid entering the chamber B3 presses on the end of the valve stem g³, and
shuts the suction valve, in the same manner as was explained in connection with
Figure 16. When the next down-stroke begins, the suction valve is therefore already
closed, and the pressure in the chamber B³ is equal to that in the delivery pipe, so
that now the delivery valve A4 experiences no resistance to opening.
Injurious leakage into or out of the chamber B³, around the valve stems 93 and g²,
can take place only while one of the pump valves is in the act of closing, because, at
other times, the pressure in the chamber B³ is the same as that in the pump cylinder.
The loss of fluid in operating the valves in this way is believed to be considerably
less than the loss from "slip" would be, with valves closed in the ordinary way.
Figure 20 shows how a single supplemental valve C³ may be employed to govern
the closing of all the suction and delivery valves of a double-acting pump, and
illustrates also a method of deriving the motion of the supplemental valve from the
main piston rod, which is applicable especially to non-rotative pumping machinery.
A pair of pump valves, A3 and A', and an intermediate pressure chamber B³, arranged
as in Figure 17, are connected to each end of the pump cylinder. An additional
port, D4, is made in the supplemental valve casing, and a separate connecting passage
led to each pressure chamber. The action of the valves at each end of the double-
acting pump cylinder is exactly the same as has been explained for the single-acting
pump. The rocking lever n³, which actuates the supplemental valve C³, is here
driven by the rod 3, which is provided with adjustable tappets 63 and 64, engaged by
a block e³, pivoted on the swinging lever d³, whose lower end is linked to the
cross head f³.
It is apparent that many changes may be made in the organizations shewn, without
departing from the invention, and it is therefore not intended to limit this invention
to any of the specific constructions shown and described, as the invention has been
shown embodied in these pumps only for the purpose of illustration, and as well
adapted to exhibit the invention in some of the forms which are considered preferable.
By the term "pumping pressure" used herein, is meant the excess of pressure
upon one side of the valve caused by the current of the fluid pumped, and tending
to open or hold the valve open during the action of the pump. It is evident that
the total pressure or force required to close the valves, will vary with the line of
movement of the valve relatively to the fluid current, and it will be understood that,
by the expressions "against the pumping pressure," and "in excess of the pumping
pressure,' it is not meant that the valve must be moved in a direction directly
opposed to that of the current, as the line of movement of the valves relatively to the
water current may be varied.
Having now particularly described and ascertained the nature of the said inven-
tion, 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 a pump valve, of means for applying and controlling a
pressure applied to said valve against, and in excess of, the pumping pressure, said
means including a column of fluid, a valve mechanism controlling said fluid, and
connections between said valve mechanism and a moving part of the pump, whereby

page_text: Baid mechanism is actuated to secure the closing of the valve, as the plunger reaches
the end of its stroke, substantially as described.
2. The combination with a pump valve, of a column of fluid having a pressure in
excess of the pumping pressure applied to said valve against the pumping pressure,
a valve mechanism controlling said fluid, and connections between said valve
mechanism and a moving part of the pump, whereby said mechanism is actuated to
apply the pressure of said fluid to the valve, to close the valve, as the plunger reaches
the end of its stroke, and to release the pressure, to permit the opening of the valve,
substantially as described.
3. The combination with a valve between the plunger, and force main of a pump,
of means for applying and controlling a pressure applied to said valve against and in
excess of the pumping pressure, said means including a column of fluid, a valve
mechanism controlling said fluid, and connections between said valve mechanism and
a moving part of the pump, whereby said mechanism is actuated to secure the
closing of the valve, as the plunger reaches the end of the stroke, substantially as
described.
4. The combination with the motor piston and plunger of a direct-acting pump,
of a valve between the plunger and force main, and means for applying and con-
trolling a pressure applied to said valve against and in excess of the pumping
pressure, said means including a column of fluid, a valve mechanism controlling said
Huid, and connections between said valve mechanism and a moving part of the pump,
whereby said mechanism is actuated to secure the closing of the valve against the
pumping pressure, as the plunger reaches the end of its stroke, substantially as
described.
5. The combination with the motor cylinder, its main and cut-off valves, and the
piston and plunger of a direct-acting pump, of a valve between the plunger and force
main, and means for applying and controlling a pressure applied to said valve against
and in excess of the pumping pressure, said means including a column of fluid, a
valve inechanism controlling said fluid, and connections between said valve mechanism
and a moving part of the pump, whereby said mechanism is actuated to secure the
closing of the valve against the pumping pressure, as the plunger reaches the end of
its stroke, substantially as described.
6. The combination with a pump valve of a duplex pump, of means for applying
and controlling a pressure applied to said valve, against and in excess of the pumping
pressure, said means including a column of fluid, a valve mechanism controlling said
fluid, and connections between said valve mechanism and a moving part of the
pump, whereby said mechanism is actuated to secure the closing of the valve, as
the plunger reaches the end of its stroke, substantially as described.
7. The combination with the force valves of a duplex pump, of means for applying
and controlling a pressure applied to said valves against and in excess of the pumping
pressure, said means including a column of fluid, valve mechanisms controlling said
Huid, and connections between said valve mechanisms and moving parts of the pump,
whereby said valve mechanisms are actuated to secure the closing of the valves as the
plungers reach the end of their strokes, substantially as described.
8. The combination with the force and suction valves of a duplex pump, of means
for applying and controlling a pressure applied to said valves, against and in excess
of the pumping pressure, said means including a column of fluid, valve mechanisms
controlling said fluid, and connections between said valve mechanisms, and moving
parts of the pump, whereby said valve mechanisms are actuated to control said fluid,
to secure the closing of the valves against the pumping pressure, as the plungers
reach the end of their strokes, substantially as described.
9. The combination with the motor pistons and plungers of a direct-acting duplex
pump, of valves between the plungers and force main, and means for applying and
controlling a pressure applied to said valves, against and in excess of the pumping
pressure, said means including a column of fluid, valve mechanisms controlling said
Huid, and connections between said valve mechanisms and moving parts of the pump,
whereby said mechanisms are actuated to secure the closing of the valves against the

page_text: pumping pressure, as the plungers reach the end of their strokes, substantially as
described.
10. The combination with the motor cylinders, the main and cut-off valves, and
the pistons and plungers of a direct-acting duplex pump, of valves between the
plungers and force main, and means for applying and controlling a pressure applied
to said valves, against and in excess of the pumping pressure, said means including
a column of fluid, valve mechanisins controlling said fluid, and connections between
said valve mechanisms and moving parts of the pump, whereby said mechanisms
are actuated to secure the closing of the valves against the pumping pressure, as the
plungers reach the end of.their strokes, substantially as described.
11. The combination of a suction and a delivery pump valve, an actuating piston or
equivalent device connected to each of said valves, a pressure chamber, a mechanically
operated supplemental valve mechanism, and passages by which fluid is alternately
admitted to and discharged from the pressure chamber in such manner as to
accelerate the closing of this suction and delivery valves, substantially as described.
12. The combination of a pump valve, a pressure chamber, a piston or equivalent
device acting upon said valve, and subjected to the pressure of the fluid in said
chamber, a inechanically-operated valve mechanism, and passages controlled by said
valve mechanism, to alternately connect said chamber with the suction and delivery
sides of the pump, to accelerate the closing of the pump valve, substantially as
described.
13. The combination of suction and delivery pump valves, a pressure chamber,
independent pistons or equivalent actuating devices acting upon the suction and
delivery valves respectively, and subjected to the pressure of the fluid in said
chamber, a mechanically operated supplemental valve mechanism, and passages
controlled by said valve mechanism, to alternately connect said chamber with the
suction and delivery sides of the pump, to accelerate the closing of the pump valves,
substantially as described.
14. The combination of the suction and delivery valves of a double-acting pump,
pressure chainbers and pistons or equivalent devices therein acting upon said valves,
a mechanically operated supplemental valve mechanism, and passages connecting said
valve mechanism with each of said chambers, and with the suction and delivery sides
of the pump, and controlled by said valve mechanism, to vary the pressure in said
chambers, by alternately connecting the chambers with the suction and delivery
sides of the pump, to accelerate the closing of the pump valves, substantially as
described.
15. The combination with the pump valves m, n, o, p, and cylinders 12, 13, 16, 17,
having pistons connected to said valves, of supply and exhaust pipes, and a valve
mechanism actuated by the pump, for connecting said cylinders alternately with the
supply and exhaust pipes, substantially as described.
16. The combination with the pump valves m, n, o, p, and cylinders 12, 13, 16, 17,
having pistons connected to said valves, of a valve mechanism V, actuated by the
pump, pipes 20, 21, 22, 23, connecting said valve inechanism with each of said
cylinders, and supply and exhaust pipes 28, 29, substantially as described.
17. The combination with pipes 24, 25, 26, 27, of a valve mechanism having cross-
over ports 6, 7, connecting said pipes in pairs, admission port 5, and valve t controlling
said ports, substantially as described.
18. The combination of an induction valve mounted within the pump barrel, a
valve stem on said valve, carrying pistons at its other end, one of said pistons being
adapted to move in a cylinder on the head of said pump barrel, and the other of said
pistons being adapted to move in a passage between said cylinder and said pump
barrel, and a supplemental valve mechanism controlling connection between said
cylinder and a source of supply of fluid pressure, for actuating said piston, to operate
said valve, substantially as described.
19. The combination of a pump barrel and a pressure chamber, valves in said pump
barrel and said pressure chamber, provided with valve stems, pistons on the other

page_text: ends of said valve stems, moving in cylinders on the heads of said pump barrel and
said pressure chambers, passages between said cylinders and said pump barrel and
pressure chamber, pistons movable in said passages, connections between said cylinders
and a source of supply of fluid under pressure, and valves interposed between said
cylinders and said source of supply of fluid pressure for controlling the influx and
efflux thereof, to actuate said piston at intervals, to operate said valves, substantially
as described.
20. The combination of an induction valve mounted upon a valve stem, a piston
upon the upper end of said valve stem, moving in a cylinder on the head of the
pump barrel, the upper face of said piston being of greater area than its lower face;
means for providing constant fluid pressure on the lower face of said piston, and
means for providing intermittent pressure upon the upper face of said piston, the
total intermittent pressure being greater than said constant pressure, whereby said
piston will be actuated against said constant pressure at intervals, to close said valve,
substantially as described.
21. The combination of induction and discharge valves connected with pistons moving
in auxiliary cylinders on the pump, fluid pressure connection between said auxiliary
cylinders and the force and suction sides of the pump, and a slide valve interposed
between said cylinders and the force and suction sides, and operated from any moving
part of said pump or engine driving the same, and adapted to alternately connect
each chamber of said auxiliary cylinder with the force and suction sides of the pump,
substantially as described.
22. The combination of induction and discharge valves, connected with pistons
moving in auxiliary cylinders on the pump, a pipe connecting the lower chamber of
one of said cylinders with the force side of the pump, a balanced slide valve connected
with said pipe, pipes connecting the upper chambers of said auxiliary cylinders with
said slide valve, pipes connecting said slide valve with the suction side of the pump,
and means for operating said slide valve for alternately connecting said pipes com-
municating with the upper chambers of said auxiliary cylinders with the force and
suction sides of the pump, substantially as described.
23. A pump discharge valve mounted upon a valve stem carrying differential
pistons at one end, a cylinder in which one of said pistons moves, a passage between
said cylinder and the force chamber in which the other of said pistons moves, the
area of the face of said last named piston acted upon by the pressure in said force
chamber being less than the area of the other piston, and not greater than the area
of the valve seat of said discharge valve, substantially as described.
24. The combination of induction and discharge valves connected with pistons
moving in auxiliary cylinders on the pump, connection between said cylinders and a
source of supply of fluid pressure, and means for alternately admitting such fluid
pressure to corresponding ends of said pistons at opposite limits of the movement of
the plunger of said pump, whereby one of said valves will be opened and the other
closed when the pump plunger reaches either limit of its movement, said faces of said
pistons acted upon by said fluid pressure tending to open said valves, being of areas
not greater than the areas of the respective valve seats of said valves, substantially
as described.
25. The combination with valve 105 and cylinder 108, having piston 107 con-
nected to said valve, of pipes 137 and 138, connecting with the cylinder on opposite
sides of the piston, and a valve mechanism operated to connect one of said pipes
alternately with the force and suction sides of the pump, substantially as described.
26. The combination with valve 105 and cylinder 108, having piston 107 connected
to said valve, of pipes 137 for applying pressure to said piston tending to open the
valve, pipe 138 for applying pressure to the opposite side of said piston 107, and a
valve mechanism controlling said pipe 138, to alternately apply and relieve the
pressure, substantially as described.
27. The combination with valve 105 and cylinder 108, having piston 107 connected
to said valve, of pipe 137 for applying pressure to said piston tending to open the

page_text: valve, pipe 138 for applying pressure to the opposite side of said piston 107, a valve
mechanism controlling said pipe 138, to alternately apply and relieve the pressure,
and small piston 107, to which the pressure in the pump chamber is applied, tending
to open the valve, substantially as described.
28. The combination with pump valve 105, and means for applying fluid pressure
to control said valve, of piston 107ª connected to said valve, and subjected to the
pressure in the pump chamber, to compensate for the difference in pressure on
opposite sides of the valve, caused by the valve seat, substantially as described..
29. The combination with valves 105, 116, and cylinder 108, 119, having pistons
therein connected to said valves, of pipes 135, 137, 138, for applying pressure to said
pistons to control the valves, and a valve mechanism controlling said pipes, to apply
and relieve the pressure on said pistons, substantially as described.
30. The combination with valves 105, 116, and cylinders 108, 119, having pistons
therein connected to said valves, of pipes connecting said cylinders with the suction
and force sides of the pump, and a piston valve or valves operated by the pump, and
controlling said pipes, to apply and relieve the pressure on said pistons, to operate the
valves, substantially as described.
31. The combination with a pump valve, of a plunger or piston projecting from its
lower or face side, a body of fluid applied to press upon said plunger or piston, and
a supplemental valve mechanism controlling said body of fluid, to vary the pressure
of said body of fluid upon said plunger or piston, substantially as described.
32. The combination of a casing containing induction and discharge valves, and an
intermediate pressure chamber, plungers or pistons formed by extensions of the valve
stems entering said pressure chamber, and a supplemental valve mechanism and
passages by which the fluid pressure in said chamber is varied, so as to accelerate the
closing of said induction and discharge valves, substantially as described.
33. The combination of a casing containing induction and discharge valves, and an
intermediate pressure chamber, independent plungers or their equivalents attached
to the said valves, and entering the intermediate pressure chamber, passages connect-
ing the intermediate pressure chamber with the fluid spaces on either side of the
induction and discharge valves, and a supplemental valve mechanism controlling the
flow of fluid through the said passages, substantially as described.
34. The combination, in a valve gearing for pumps, of an induction valve, and a
discharge valve communicating with the pump cylinder on the same side of the main
plunger, a pressure chamber distinct from the pump chamber containing a body of
fluid which presses upon the said valves in a direction tending to close the induction
valve and to open the discharge valve, and means for varying the said pressure during
the stroke of the pump, so as to accelerate the closing of each of said valves, sub-
stantially as described.
35. The combination with the valves A³, A* and intermediate pressure chambers B³,
of plungers or pistons g³, gt acting on said valves, and acted upon by the fluid in said
chamber, passages E³, F³, a valve chamber connected with said pressure chamber and
passages E3, F3, and a valve mechanism for connecting said chamber with the fluid
on the suction and discharge sides of the pump valves alternately, substantially as
described.
36. In a double-acting pump, the combination with the plungers p³, of induction
and discharge valves A3, A4 and intermediate pressure chambers B' for the respective
plungers; plungers or pistons acting on said valves, and acted upon by the fluid in
said chambers; a valve mechanism controlling the admission and discharge of fluid
from each of said pressure chambers; and passages E³, F³ controlled by said valve
mechanism, to connect said pressure chambers with the fluid on the suction and
discharge sides of the pump valves alternately, substantially as described.
.
37. A pumping engine substantially as shown and described in connection with
Figures 1 to 9 of the accompanying drawings.
38. A valve movement for pumps, substantially as shown and described in connec
tion with Figures 10 and 11 of the accompanying drawings.

page_text: 39. A valve movement for pumps, substantially as shown and described in connec-
tion with Figures 12 to 15 of the accompanying drawings.
40. A valve movement for pumps, substantially as shown and described in connec-
tion with Figures 16 to 20 of the accompanying drawings.
Dated this 26th day of July 1898
NEWTON & SON,
Agents for the Applicant.