Improvements relating to Steam and other Pumps.
Year: 1897

page_text: Date of Application, 15th June, 1897-Accepted, 4th Sept., 1897
[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 relating to Steam and other Pumps.
1, 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, and an improved method of closing pump valves, and especially to secure a
more uniform action of steam or power pumps, and to increase the speed at which
they can be operated successfully.
While the main features of the invention are of general application in pumps of
all classes, the invention is of special application to direct-acting steam pumps, or
pumping engines, in which the improvements constituting the invention co-operate
with other features of the construction, to secure certain special results not attained
in other pumps, and the invention will therefore be generally described as applied to
steam pumps, or pumping engines of this class. In this class of pumps, as is well
known, the motor pistons are connected to the rods which carry the corresponding
pump plungers, in such manner that the piston and plunger are free to move in
either direction, according to the side of the piston upon which the pressure is
greater.
It has been customary to provide pumps of this class with some means by which
the piston and plunger are gradually arrested at the end of the stroke in either
direction, thus avoiding the danger of damage to the pump by more or less violent
contact of the piston with the heads of the cylinder. Numerous devices have been
proposed for this purpose, but that most generally adopted in practice consists of
double steam ports in the cylinder so arranged that the exhaust port is closed by
the piston just before it reaches the end of its stroke in either direction, thus causing
the piston to be arrested gently, by cushioning upon a small portion of the exhaust
steam remaining in the cylinder. This method has been found satisfactory at the
speeds at which pumps of this class are usually run. Wherever this speed is increased,
however, the momentum of the moving parts becomes sufficient to compress the
steam thus imprisoned between the exhaust port and the cylinder head, to a
pressure which causes a rebound or recoil of the moving parts of the pump.
recoil is due to the pressure in the cushion acting upon the piston, plus the pressure
in the force main acting upon the plunger, the pressure in the force main being
communicated to the plunger through the force valves, which at that moment of the
stroke have not had time to close. The effect of this recoil is to cause the water in
the force chamber to flow rapidly through the force valves into the pump chamber,
producing a current which tends to slam the force valves violently to their seats.
The suction valves at the opposite end of the plunger also are slammed by the
pressure produced by the recoil movement of the plunger. The violence of
This

page_text: this slam increases with the speed of the pump, and soon becomes an element of
danger.
One of the specific objects of the present invention is to provide means whereby,
when the plunger arrives at the end of the stroke, this recoil is avoided,
and all backward movement of the plunger prevented until it begins its return
stroke.
With this pump, in which the piston is stopped entirely by the cushion, it is
evident, as the momentum of the moving parts increases with the velocity, that the
cushioning pressure upon the ends of the steam cylinder is very great at high
speeds, and that the danger of damage above referred to can be prevented only by
employing a high steam cushion at all times, or providing some means by which
the amount of cushion can be regulated, and increased or decreased, with the speed
of the pump.
In the use of stea:n cushions, therefore, it is customary to provide
some means by which the amount of steam retained is varied in accordance with the
speed of the pump, and for this purpose a small outlet is generally provided at the
end of the cylinder, and this outlet controlled by a "relief valve." By the adjustment
of this relief valve, the amount of steam retained can be varied, as desired, so as to
secure the filling up of the clearance spaces, and the exact adjustment of the length
of stroke, with the proper cushioning of the piston at different speeds, without the
employment of a permanently large cushion.
A further object of the invention is to provide means by which the piston and
plunger may be stopped wholly or partially by pressure acting against the plunger
in the water cylinder toward the end of the stroke, thus avoiding the necessity for
adjustment of the steam cushion, in accordance with the speed of the pump,
and rendering it possible to employ only a moderate steam cushion at all
speeds.
The piston and plunger may be stopped entirely by applying increased pressure
upon the plunger at the end of the stroke, but 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, and secure the immediate action of
the piston, when the live steam is admitted, upon the reversal of the valves.
A further object of the invention is to provide means for positively controlling
the water valves, and especially to provide means by which these valves shall be
gradually and positively closed by pressure during the latter part of the stroke of
the plunger, the closing of these valves thereby exerting a gradually increased
stopping pressure upon the plungers.
An improved method of closing a pump valve, either suction or force, consists in
applying to said valve, against the pumping pressure, a pressure in excess of the
pumping pressure, and it is preferred to vary the pressure thus applied gradually
during the stroke of the punip plunger, so as to secure the gradual closing of the
valve against the pumping pressure, and the special objects pointed out above are
attained by thus closing the force valves or an auxilliary valve or valves between
the plunger and force main, so that the pressure in the force main is cut off from the
plunger of the pump at the end of its stroke, with the results that no recoil of the
plunger takes place, and the plunger is stopped wholly or partially by the pressure of
the water within the pump cylinder. By the term "pumping pressure is meant
the excess of pressure upon the pump cylinder side of the valve, tending to open or
hold the valve open during the action of the pump. This pressure applied to the valve
may be supplied from any suitable source in single or duplex pumps, and any suitable
means may be used to control it in accordance with the action of the plunger, so as to
secure the results desired, but in duplex pumps it is preferred to transmit a fluid
pressure varying with the movement on one side of the pump to the valve or valves
on the opposite side, so as to control the valve or valves in such a manner as to secure
their closing in the manner desired.
"
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 water current, and it will be

page_text: understood that by the expressions "against the pumping pressure" and "in excess
of the pumping pressure " I do not mean that the valve must be moved in a direction
directly opposed to that of the current, but intend to cover broadly all constructions
in which the valves are closed by a fluid pressure acting in opposition to the pumping
pressure, and of sufficient amount to close the valve, whatever be the line of movement
of the valve relatively to the water current.
It is preferred to apply the closing pressure directly to the force valves, so as to
secure their gradual and positive closing in front of the plunger as the latter reaches
the end of its stroke, and it is preferred to apply this pressure also to the suction
valves, to secure their closing behind the plunger at or about the same time, but this
closing pressure may be applied only to the force valves, or to an auxiliary valve or
valves controlling communication between the force main and the water cylinder, so
as to secure the results desired, and similar auxiliary valves may be used also with the
suction valves.
The varying fluid pressure that controls the valves may be so applied as to close
the auxiliary or main valves, or the valves may be closed by a constant pressure from the
main or other suitable source, or by the pressure of a spring or weight, and the varying
fluid pressure employed to control the operation of the valves by such constant pressure,
but it is preferred to use the force main pressure as the constant pressure, and use as
the varying pressure, the pressure in the pump cylinder, this varying pressure being
applied alternately from in front of, and behind the pump plunger, and, in duplex
pumps from the pump cylinders on the opposite side of the engine. The varying
fluid pressure, moreover, may control the operation of the valves either by opposing
the constant pressure, so that the closing pressure upon the valves varies with the
ratio of the varying to the constant pressure, or the varying pressure may operate
a valve by which the constant pressure is controlled, as desired, to secure the closing
of the valves, as above described.
In attaining the highest speeds with a steam pump provided with positive water
valves acting as described, to cause a gradual increasing pressure to act against the
plunger, it may be found, in some cases, that the available pressure is not sufficient
to thus close the valve, because as it begins to close, the speed of the plunger is
lessened, which is immediately followed by a packing of the steam behind the steam
piston causing an increase of steam pressure. The increase of steam pressure thus
caused may exceed the available power for operating the water valves, and thus prevent
their closing. When a very high speed is desired, therefore, it is advisable to provide
the steam cylinder or cylinders with cut off valves, which shall operate to cut off the
admission of steam to the cylinder late in the stroke, so that the water valves can be
positively closed, and the plunger and piston stopped, without the packing of the
steam in the steam cylinder.
A
In the ordinary low duty pumps now in use, the cut off valves operate at about five
sixths stroke, it being found necessary to continue the admission of the steam to this
late point in the stroke at the speeds at which these pumps are generally run.
higher economy would be attained by cutting off earlier in the stroke, and with the
positive water valve and high speed rendered possible thereby, this is practicable, as
the high piston speed and momentum acquired by the piston and plungers 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.
As the invention is especially adapted for use in duplex direct-acting steam pumps,
in which the valves on one side may be controlled from the opposite side, as above
described, and consists, in part, in the construction and arrangement of connections by
which the valves are controlled in such pumps, the invention will be illustrated in
connection with duplex pumps, and a full description of constructions embodying the
invention in the preferred form will now be given in connection with such an
illustration, and the method and features of construction forming the invention
specifically pointed out in the claims.
For a full understanding of the invention, a detailed description of single and duplex
pumps embodying the improvements in their preferred form will now be given,

page_text: reference being had to the accompanying drawings forming a part of this specification,
and the method and features of construction forming the invention specifically
pointed out in the claims.
In the drawings:
Figure 1 is a side elevation of a simple crank power pump provided with the
improved valve movement in one of its preferred forms with a constant pressure applied
to close the valves and controlled by a varying pressure.
Figure 2 is a plan view of the same.
Figure 3 is a rear elevation.
Figure 4 is a section on the line 4-4 of Figure 2, on an enlarged scale.
Figure 5 is a side elevation of the water end, similar to Figure 1, shewing a single
pipe for transmitting the varying pressure.
Figure 6 shews a modification of the same.
Figure 7 is a sectional side elevation of a duplex direct-acting steam pump, with
the valves closed by a constant pressure controlled by a varying fluid pressure, the
section being taken through the steam cylinder on the following side.
Figure 8 is a plan view of the water end of the same.
Figure 9 is a section on the line 9-9 of Figure 8, on an enlarged scale.
Figure 10 shews a modification in the connections with the pump cylinders.
Figure 11 shows a modification employing auxiliary force and suction valves.
Figure 12 is a longitudinal section of a duplex direct-acting steam pump, shewing
the valves closed by a varying fluid pressure from the opposite side of the pump, the
section of the water end being taken on the line 12-12 of Figure 13, and of the
steam end centrally through the steam cylinder on the following side of the pump.
Figure 13 is a plan view of the water end.
L
..
:
Figure 14 is a rear elevation of the water end.
Figure 15 is a longitudinal section, on the line 15-15 of Figure 13.
Figure 16 is a cross section on the line 16-16 of Figure 13.
Figure 17 is a sectional elevation of a pump shewing a construction employing a
single valve-controlling motor cylinder for each side of the pump.
Figure 18 is a plan view of the water end of the same.
Figure 19 is a sectional elevation looking to the right from line 19-19 in
Figure 17.
Figure 20 is a section similar to Figure 17, except that the auxiliary valves are
placed inside the force valves.
Figure 21 is a plan view of the water end, shewing another construction in which
the valves are closed by a constant pressure opposed by the varying pressure.
Figure 22 is a section looking to the left, on the line 22-22 of Figure 21.
Figure 23 is a section of the water end, shewing a construction in which the varying
pressure operates a valve to control a constant pressure closing auxiliary force and
suction valves.
Figure 24 is a plan view of a construction with the varying pressure transmitted
from the steam cylinders; and Figure 25 is a detail of a modification hereinafter
referred to.
Referring now particularly to Figures 1 to 4, the engine shewn is, as to its general
construction, a common form of crank engine, A being the gear, B the crank disc,
C the connecting rod, D the plunger rod, E the plunger, F the water cylinder, G, H,
the force and suction mains, and I, K, the force and suction chambers, communication
between the pump cylinder and these chambers being controlled by force valves a
and suction valves 6 at the opposite ends of the cylinder. These parts form an
ordinary double-acting crank pump.
t.
1
Referring now to the parts embodying this invention, a small motor cylinder 10, 11,
is mounted above each of the force and suction valves respectively, the valves being
actuated by motor pistons 12 moving in said cylinders, and carried by the valve
stems 13. The motor cylinders 10, 11, are entered above the pistons 12 by pipes 14,
through which a constant pressure is transmitted to the motor pistons, tending to
close the valves. These pipes 14, are shewn as connected with the force main G, but

page_text: may be connected to any other suitable source of pressure either within or without
the pump.
On the opposite side of the pistons 12 from the pipes 14, transmitting the constant
pressure, the motor cylinders 10, 11, are connected with the water cylinder in the
following manner:-The pipes 15, 16, communicate with the water cylinder at opposite
ends, and have branches 17, 18, and 19, 20, entering the motor cylinders 10, 11,
these pipes connecting each end of the water cylinder with the inotor cylinder
controlling the force valve at the same end of the pump, and with the motor cylinder
controlling the suction valve at the opposite end. The pipes 16, 15, enter the pump
cylinder at points within the path of the pump plunger, and the pump plunger, as it
approaches the end of its stroke in either direction, will pass the port of one of the
pipes, and leave it uncovered behind it, so that the suction pressure in the cylinder is
transmitted through the saine to the motor cylinders above the force and suction valves
controlled thereby.
For the purpose of adjusting the time at which the pressure from the pump cylinder
acts upon the piston in the motor cylinder, each of the pipes through which the
pressure is transmitted, is provided with a throttle valve I. In the construction shewn,
this enables the times at which the pressure acts on the force and suction valves to be
adjusted relatively to each other, which is especially desirable when a single connec-
tion is made with the pump cylinder for a force and suction valve, as in the construction
shewn. It will be understood, however, that there may be two openings into the
pump cylinder for each motor cylinder, so that the connections for the force and
suction valves are independent of each other. The throttle valves, or other suitable
adjusting means, will still be used, however, to secure the proper timing of the action
of the motor cylinders upon the valves.
The operation of this construction is as follows:-
As the plunger E moves to the right from the position shewn in Figures 1 to 4, the
pressure in front of the plunger is transmitted through pipes 16 and branches 19, 20,
to the motor cylinders 10, 11, above the force and suction valves, respectively in frout
of and behind the plunger. This pressure counter-balances the constant pressure
admitted to the other side of the pistons 12 through pipes 14, and these valves are
opened by the water current. This continues until the plunger E has passed-the
pipe 16 and opened the latter behind it, when the pressure in the pipe 16 and below
the pistons 12 in cylinders 10, 11 is reduced to that of the suction, and the valves are
closed by the excess of the constant pressure above the pistons, it being understood
that the pressure upon the opposite sides of the valves a, b, independently of the
pistons, is the same, so that a slight excess of pressure suffices to close them.
1
As the plunger is reversed, and moves from right to left, the pressure in front of the
plunger is again transmitted through pipe '6 and branches 19, 20, equalizing the
pressure in the motor cylinders above the tons, but the force valve is closed behind
the plunger by the force pressure, and the suction valve in front of the plunger by the
pressure in the pump cylinder produced by the plunger.
As the plunger is reversed, however, the pressure in front of the plunger is
transmitted also through the pipe 15 and branches 17, 18, to the motor cylinders 10, 11,
above the force and suction valves respectively in front of and behind the plunger,
and the pressure on the opposite sides of the motor pistons 12 being equal, the valves
are opened by the water current. This operation is repeated at each stroke of the
plunger.
The time of closing of the valves may be adjusted as desired, by varying the position
of the pipes 15, 16, relatively to the plunger E, so that any desired operation of the
valves may be secured. The time and rapidity of closing of the valves may also be
adjusted conveniently by means of the throttle valves 1, the passage of the water
through the pipes being controlled thereby as desired.
While the pipes have been shewn transmitting the constant pressure from the
force main, and it is preferred that constant pressure should be applied thus, or from
an outside source of pressure, when the valves are closed by a constant pressure
controlled by a varying pressure, it will be understood that the pistons may be open

page_text: above to the air, and air pressure be employed as the constant pressure, if desired,
this necessitating only an increase in the size of the motor pistons, depending upon
the work to be perforined. It will be understood, also, that it is not necessary that
the constant pressure should be that of a fluid, but that a spring or weight may be
substituted therefor, if desired.
Although the construction shown will probably he found preferable, as it reduces
the size of the plunger, it is not necessary to employ two pipes communicating with
the water cylinder. In Figure 5, I have shewn a construction in which a single
pipe 21 communicates with the water cylinder midway of its length, the branches 17,
18 and 19, 20 all communicating with this pipe. In this construction, the length
of the plunger E is nearly the length of the stroke, as shewn in Figure 5.
The operation of this construction is as follows:-
As the piston E reaches the end of its stroke, the port of pipe 21 is uncovered
behind it, and the pressure below all the motor pistons 12 is the suction pressure,
and the valves are all closed by the constant pressure.
As the plunger commences its return stroke, the pressure in front of the plunger
is transmitted, through the pipe 21 and its branches, to all the cylinders 10, 11, and
the constant pressure is counterbalanced therein. The force and suction valves
respectively in front of and behind the plunger are then opened by the water current,
while the force and suction valves respectively behind and in front of the plunger,
are closed by the pressure of the force main, and in the pump cylinder. The result,
therefore, is substantially the same as with the construction previously described.
With this construction of a single pipe communicating with the water cylinder,
the improvements may be applied to the common plunger and diaphragm or ring
construction of pumps, the pipe 21 being placed within the ring or diaphragm, as
shewn in Figure 6, and communicating with the pump cylinder through a circular
port, or series of ports, as preferred.
Referring now to Figures 7, 8, and 9, the duplex direct-acting steam pump shewn
therein as embodying the improvements will be described. The pump is, as to its
general construction of a common form, consisting of two steam cylinders L,
provided with pistons M connected by piston rods N to the plungers O, moving in
the water cylinders Q, P, on respectively the leading and following sides of the
pump. In the operation of duplex pumps, 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 piston is always in advance, in
whichever direction the two pistons are moving, and in accordance with established
practice, the terms "leading and following" refer respectively to the sides of the
pump, the pistons of which lead or follow when both are moving in the same
direction.
The steam cylinders are provided with the usual valve gear, consisting of rock
shafts C, levers d, and valve rods e, by which the main valves f on each side of the
pump are operated from the piston rods on the other side, in the manner common in
duplex pumps. The steam cylinders are preferably provided with separate induction
and exhaust g, h, so that as the pistons M, near the end of their strokes in either
direction, they cover the exhaust port h, and confine a small amount of exhaust
steam in front of them in the cylinder, 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, as stated above,
all cushioning of the steam pistons may be omitted, and the pistons and plungers
be stopped by water pressure only. The induction ports g are controlled by cut-off
valves 8 operating to cut off the steam as above described. This construction
of rotary cut-off valves, and their operating connections, are well known, and need
not be particularly described herein. It will be understood, however, that any other
form of cut-off valves and operating connections may be substituted, if desired.
The water end of the pump consists of the water cylinders Q, P, on the leading
and following sides respectively, the suction and force mains R, S, and their
chambers T, U, communication between the cylinders and these chambers being

page_text: controlled by force valves k, l, and suction valves m, n, on respectively the leading
and following sides of the pump.
Referring to the parts in which the invention is embodied, above each of the
force and suction valves is mounted a motor cylinder, the motor cylinders above the
force valves on the leading side of the pump being numbered 22, 23, and on the
following side of the engine 24, 25, and the motor cylinders ab we the suction valves
on the leading side being numbered 26, 27, and those on the following side 28, 29,
at the opposite ends of the water cylinders respectively. Each of the valves is
controlled by a piston 30 moving in the corresponding notor cylinder, these pistons
being carried by the valve stems 31.
The constant pressure is transmitted from the force main to the motor cylinders
in the following inanner :-The valve stem 31 of each of the force valves is hollow,
and, as shewn in Figure 9, is provided, at its lower end, with a series of perforations 2,
opening into the force chamber T, and, at its upper end, above the piston 30, with a
series of perforations 3 opening into the motor cylinder. The constant pressure is
transmitted from the force chamber T to the cylinders above the suction valves by
pipes 32, as shewn in the same figure.
The motor cylinders below the pistons 30, are connected with the water cylinders,
so that the varying pressure therein is communicated to the motor cylinders in the
following manner :- -Pipes 33, 34, extend from the opposite ends of the water
cylinder, on the leading side of the pamp, to the opposite side, and communicate
respectively with the motor cylinders 24, 25, above the force valves on the following
side; and, by branches 35, 36, also communicate respectively with the motor
cylinders 29, 28, upon the following side, so that the pressure in the water cylinder
upon the leading side of the pump is transmitted to the force and suction valves
upon the following side of the pump, but the connections to the suction valves are
reversed, so that the pipes 33, 34, control the force valves at the corresponding ends
of the water cylinder on the following side, and the suction valves at the diagonally
opposite ends of the cylinder. Pipes 37, 38 connect the opposite ends of the water
cylinders 23, 22, above the force valves, at the diagonally opposite ends of the water
cylinder, on the leading side of the pump, and, by branches 39, 40, also communicate
respectively with the notor cylinders 26, 27, above the suction valves, at
corresponding ends of the water cylinder, on the leading side, so that pipes 37, 38,
from the following side of the pump control the force valves at the diagonally
opposite ends of the water cylinder on the leading side, and the suction valves at
the same end of the water cylinder.
'
The peration of the duplex pump is as follows:-It is to be remarked that, as
shewn in the drawings, the pump is at rest, and both sides are on centre. This
is not a position that the parts of the pump will assume when in actual operation,
but has been adopted for the purpose of illustration.
In describing the operation, it will be assumed that the piston M of the leading
side of the pump is started from left to right, the piston on the following side
being in the position of, say, five-sixths stroke from right to left. As the piston
on the leading side moves to the right, the water in front of the plunger on
that side, will be forced past the valves 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 m behind the plunger. As the piston and plunger
approach the end of their stroke, the cut-off valve s will operate to cut off the
steam behind the piston, the piston will cover the exhaust port h and
cushion itself upon the steam confined in the end of the steam cylinder beyond
this port, and the piston and plunger will 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 on the following side of the pump will
have completed its stroke in the opposite direction, and will start in the same
direction as that in which the piston on the leading side is then moving, that is,
from left to right, the two pistons moving in the same direction, until the piston

page_text: upon the leading side has completed its stroke, when the motion of the latter is
reversed, and it returns partially during the forward stroke on the following side.
This is the usual operation in duplex pumps.
It will readily be seen that, if no special means are provided for closing the valves,
except the springs usually employed, the force valves will be open at the time
the plungers are stopped, so that the full pressure of the water in the force main
and force chamber will be permitted to act for a short period of time upon the
plunger. If the speed of the pump be such that the momentum of the moving
parts compresses the steam between the piston and cylinder head sufficiently, the
back pressure of this steam cushion, together with the pressure of the force main
upon the plunger, will cause a rebound or recoil of the piston and plunger, thus
producing a rapid current from the force main, through the force valves, into the
water cylinder, which slams the force valves violently to their seats, as above
described. This recoil of the plunger slams also the suction valves at the other end
of the plunger, which have not had time to close. It will be seen that, besides the
objectionable noise caused by this action, it produces a jar upon the pump
which increases with the speed, and practically prevents the attainment of high
speeds.
Apart from the necessity of overcoming this combined action of the cushion and
pressure from the force main, moreover, it is desirable that means should be
provided for closing the valves positively, as the plunger reaches the end of its
stroke, so that certainty and promptness in the closing of the valves is secured.
This closing is preferably gradual, so that an increasing cushioning pressure is
applied to the plunger, and the plunger is stopped slowly, without shock, the
cushioning pressure required in the steam end being reduced thereby.
In the present organisation, the pressure from the force main is transmitted
through the hollow valve steams 31 to the motor cylinders above the pistons 30
controlling the force valves, so that the pistons are constantly subjected to the
pressure of the force main, tending to move them in a direction to close the force
valves. The force pressure is transmitted also to the pipes 32 from the force
chambers T to the motor cylinders mounted above the suction valves, so as to tend
to close the suction valves in the same manner as the force valves.
As already explained, the pipes transmitting the varying pressure from the pump
cylinder on one side of the engine, to the motor cylinders upon the opposite side,
enter the motor cylinders below the pistons, so that their pressure is opposed to the
pressure from the force main above the pistons, this varying pressure being equal
to the pressure from the force main when transmitted from in front of the plunger,
but reduced to the suction pressure when the plunger has passed the ports by
which the pipes transmitting the varying pressure communicate with the pump
cylinders.
As the plunger on the leading side commences its stroke from left to right, as
before described, the pressure in the water cylinder Q in front of the
plunger, is transmitted for
a short time through the pipe 33 and branch 35
to the motor cylinders 24, 29, below the pistons controlling the force valve / and
suction valve n, respectively in front of and behind the plunger on the following
side of the pump, counterbalancing the force pressure above the pistons in those
cylinders, and these valves are opened by the water current as the plunger O, on
the following side, continues its stroke from right to left the one-sixth stroke still
remaining.
As the plunger on the leading side continues its stroke, however, it soon passes
and uncovers behind it the port of pipe 33, so that the pressure in pipe 33 and
branch 35, and consequently that below the pistons in the motor cylinders 24, 29,
is reduced to the suction pressure, and the force valve and suction valve n, respectively
in front of and behind the plunger on the following side of the pump, which are
controlled by these pistons, are gradually and positively closed, just as the plunger
on this side reaches the end of its stroke from right to left. The pressure in front
of the plunger upon the leading side is still transmitted through the pipe 34 and

page_text: branch 36 to the motor cylinders 25, 28, below the pistons, so that the constant
pressure in these cylinders is counterbalanced, and as the plunger on the following
side is reversed, and moves from left to right, the force and suction valves respectively
in front of and behind the plunger, which are controlled by the pistons in these
cylinders, are opened by the water current.
On this reversal of the plunger on the following side, the pressure in front of
the plunger is transmitted for a short time through the pipe 37 and branch 39 to the
motor cylinders 23, 26, controlling the force and suction valves respectively in front
of and behind the plunger on the leading side, and counterbalances the constant
pressure therein, so that these valves remain open as the plunger on the leading side
continues its stroke from left to right. The plunger on the following side, however,
soon passes, and uncovers behind it the port of pipe 37, and the movement of the
water, and consequent transmission of the pressure through pipe 37 and branch 39
to the motor cylinders 23, 26, is so adjusted, that the pressure below the pistons in
the motor cylinders 23, 26, is reduced to that of the suction at the proper time, so
that the force and suction valves respectively in front of and behind the plunger on
the leading side, which are controlled by the pistons in these motor cylinders, are
gradually and positively closed by the constant pressure, as the plunger on the
leading side reaches the end of the stroke.
As the plunger on the leading side is reversed, and moves from right to left, it
operates by proper adjustment of the passage of the water, and consequent
transmission of the pressure, to secure the gradual and positive closing of the force
and suction valves respectively in front of and behind the plunger on the following
side, as this plunger reaches the end of its stroke.
The operation described is constantly repeated during the action of the pumps.
The time of closing of the valves may be adjusted, in the construction of the
pump, by proper determination of the points at which the pipes transmitting the
varying pressure enter the pump cylinders, or by proportioning the sizes of the pipes
and motor cylinders. It will, however, be found convenient, and may in some cases
be necessary, to provide means whereby the passage of the water through the pipes
shall be retarded, or the operation of the pistons and valves otherwise controlled, so
that the valves shall not be fully closed until the plunger reaches the end of its
stroke. This may conveniently be done by means of the throttle valves 1 upon the
pipes, by which the varying pressure is transmitted, the passage of the water, and
consequently the variations of the pressure below the motor pistons, being thus
adjusted as desired.
In the constructions thus far described, the varying pressure below the pistons is
controlled by the passage of the plungers in the pump cylinders, over the ports, by
which the pipes transmitting the varying pressure communicate therewith, but this
is not necessary. It may be advisable to employ an organisation for duplex engines
similar to that previously described, except that the pipes transmitting the varying
pressure are not opened and closed by the plunger, so that the change from force to
suction pressure is made during the stroke of the plunger, but the pipes are in
constant free communication with the pump cylinders, and the change from force to
suction pressure is made on the reversal of the plungers at the ends of their strokes
in either direction.
In Figure 10, I have shewn such a construction applied to a pump of the common
diaphragm ring and plunger construction. The arrangement of pipes is identical
with that shewn in Figures 7 to 9, and previously described, except that the pipes
transmitting the varying pressure communicate freely at all times with the pump
cylinder, they being shewn as communicating above the pump cylinders with the
passages leading to the force and suction chambers, although it will be understood
that they may open into the pump cylinders at any points upon the opposite sides of
the central diaphragm.
The operation of this construction is substantially the same as that of the duplex
engine previously described, except that the pressure below the pistons 30 in the
motor cylinders above the force and suction valves, is changed from force to suction,

page_text: and vice versa, only as the plungers are reversed on completing their strokes in either
direction. As previously described, the variations of the pressure below the motor
pistons are controlled by the throttles 1, so as to secure the proper closing of the
valves by the force pressure above the pistons, when the pressure below the pistons is
reduced by the reversal of the controlling plunger, but any other suitable means
may be used for this purpose.
In the organisation thus far described, the motor pistons control the force and
suction valves directly, but, as state 1 above, auxiliary valves may be provided between
the pump cylinder and the force and suction mains, either between the force and
suction valves and the mains, or between the pump cylinders and the force and
suction valves.
In Figure 11, I have shewn such an organisation in which the construction is
similar to that shewn in Figure 4, except that the force and suction chambers
communicate with the pump cylinder by separate passages, and these passages are
controlled by force and suction valves o, p, of the usual construction, the valves a, b,
of the construction in Figure 2, which are controlled by the pistons 12, being
auxiliary valves.
The use of an auxiliary valve placed between the cylinder and the main, on either
side of the main valves, does not in any respect alter the function of the main
valves. In case the auxiliary valves on the force side become obstructed at any time,
or held from their seats 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, the only result, in the arrangement
described, being a noisy action of the pump until the auxiliary valve has been
relieved. In case of any accident or breakage to the auxiliary force valve, it may be
removed for repair, during which interval the pump may be operated as in the
common construction, at a somewhat slower piston speed than is customary with the
auxiliary valve in commission.
It is evident that, with the auxiliary valve as shewn in Figure 11, substantially
all the advantages of the positive action of the force and suction valves are obtained,
the gradual closing of the auxiliary valve closing the force main, & exerting a
gradual stopping pressure upon the plunger.
Referring now to the construction shown in Figs. 12 to 16, in which the varying
fluid pressure is applied to close the valves, the corresponding main parts of the
pump are lettered similarly to the parts of the pumps already described.
The water cylinders are provided with the usual force valves k, l, m, n, and
suction valves o, p, q, r, the force valves, l, and suction valves 0, P,
communicating respectively with the water cylinder at the end next to, and furthest
from, the steam end, on the leading side of the pump, and the force valves m n
and suction valves q r corresponding thereto on the following side of the pump.
Each of the force valves k, l, m, n, is connected to the piston rod 1 of a piston 2,
these pistons moving in small motor cylinders 11, 12, 13, 14, mounted above the
respective force chambers. The suction valves o, p, q, r, are similarly connected by
the piston rods 3 to pistons 4 moving in cylinders 15, 16, 17, 18, mounted above the
respective suction chambers.
These small cylinders are connected to the water cylinders on the opposite side of
the pump as follows:- -The cylinders 11, 12, controlling the force valves k, l, on the
leading side of the pump, are connected by means of the pipes 19, 20, to the water
cylinder Q on the following side of the pump, these pipes communicating with the
water cylinders on the same end of the plunger as their respective valves k, l, controlled
thereby. The cylinders 15, 16, controlling the suction valves o, p, on the leading
side of the pump, are connected by pipes 21, 22, to the pipes 20, 19, and are so
arranged that the suction valves are controlled from the diagonally opposite ends of
the plunger on the opposite side of the pump. Thus, the pressure on the following
side of the pump controls both the force and suction valves on the leading side of the
pump through the pipes 19, 20, but the force valves are controlled by the pressure at
the ends of the plunger which correspond to those at which the said valves are

page_text: located relatively to the plunger on their own side of the pump, while the suction
valves are controlled by the pressure at the diagonally opposite ends of the
plunger.
The cylinders 13, 14, controlling the force valves m, n, on the following side of the
pump, are connected by means of pipes 24, 23, to the water cylinder on the leading
side of the pump, these pipes being reversed in crossing, so that the force valve at one
end of the plunger is operated by the pressure in the opposite water cylinder at the
diagonally opposite end of the plunger on that side. The cylinders 17, 18, controlling
the suction valves q, r, are connected by pipes 25, 26, to the pipes 23, 24, these pipes
being so arranged that the suction valves are operated by the pressure at the
corresponding ends of the plunger in the opposite water cylinder. Thus, the pressure
on the leading side of the pump controls both the force and suction valves on the
following side of the pump, through the pipes 23, 24, but the force valves are
controlled by the pressure at the ends of the plunger diagonally opposite the ends at
which the valves are located relatively to the plunger on their own side of the pump,
while the suction valves are controlled by the pressure at the corresponding ends of
the plunger.
Each of the pipes transmitting the pressure from the water cylinders to the small
motor cylinders, is provided with a hand valve 5, by which the passage of the water
through the pipes, and consequently the time or rapidity of movement of the force
and suction valves, can be accurately adjusted. Any other suitable means for
adjusting the time or rapidity of movement of the valves may be used. For
instance, the stroke of the pistons in the motor cylinders may be varied, as shown
in Fig. 25, the upward movement of the pistons 2 being limited by adjustable
stops 54, so that the distance through which the valve moves, in closing, may be
varied as desired. The pipes transmitting the pressure from the water cylinders
enter the motor cylinders above the pistons 2. Below the pistons, the cylinders are
preferably connected to the suction inain by means of pipes 6, for a purpose bereafter
stated. The arrangement of pipes is fully shown in the drawings, especially in
Figs. 13, 14, and 15, and will be readily understood from the above statement.
The operation of this construction is as follows:-
As the plunger O, on the leading side, advances to the right, the pressure in the
water cylinder P in front of the plunger is transmitted through the pipe 24 to the
cylinder 13 and operates the piston 2, to positively and gradually close the force
valve m on the following side of the pump in advance of the plunger 0, which is then
just completing its stroke from right to left. This pressure is transmitted also
through pipes 24 and 26 to cylinder 18, and operates the piston 4 to positively close
the suction valve on the following side, behind the plunger.
The plunger on the following side having completed its stroke from right to left,
returns from left to right, and as the plunger O on the leading side completes its
stroke from left to right, the pressure in the water cylinder Q in front of the plunger
is transmitted through pipes 20 and 22 to the cylinder 12, 15, and operates the
pistons 2, 4, to close the force valve and suction valve o, respectively in front of and
behind the plunger O on the leading side.
As the plunger on the leading side is reversed, and moves from right to left, the
pressure in advance of the plunger is transmitted through the pipes 23 and 25 to the
cylinders 14, 17, and closes the force valve n and suction valve q, as the plunger O
on the following side completes its stroke from left to right, and as the plunger O on
the following side reverses, it closes, through pipes 19, 22, aud cylinders 11, 16, the
force valve and suction valve p, as the plunger on the leading side completes its
stroke from right to left.
This operation is constantly repeated during the operation of the pump.
It will be seen that as the inovement of one of the plungers is reversed, the
pressure upon one set of force and suction valves upon the opposite side of the pump
is released, and the pressure transmitted to the other set of valves.
As the pressure
is released upon the force and suction valves, they are operated by the pressure of the
water acting under them, as usual in pumps.

page_text: If the small motor cvlinders were closed at their lower ends, the air contained
therein would produce an upward pressure upon the pistons, which must be
overcome by the pressure from the water cylinder, it being impracticable to maintain
a vacuum in the cylinders. Moreover, a certain amount of water must, in time, pass
the pistons 2, 4, and collect in the lower ends of the cylinders. The lower ends of
the cylinders, therefore, are preferably entered by the pipes 6 previously referred to,
which form drip tubes. The drip from the cylinders will be relieved by these pipes,
if they open to the air, but as the pressure of the air is generally in excess of the low
pressure on the suction side of the plunger, the pipes 6 are preferably connected to
the suction main, as shown in Fig. 13, thus producing an equilibrium of pressure
upon the opposite sides of the pistons 2, 4, when the pressure from in front of the
plungers is removed therefrom.
As the pump is generally constructed and adjusted so that the plunger on one
side commences its stroke somewhat prior to the completion of the stroke then being
made on the other side of the pump, and as the pressure in advance of the plunger
is at once transmitted to the pipes connected with the opposite side, it may, in some
cases, be necessary to provide some means whereby the transmission of the pressure
through the pipes shall be retarded, or the operation of the pistons and valves
otherwise controlled, so that the valves shall not be fully closed until the plunger
reaches the end of its stroke. This adjustment may be made permanently in the
construction of the pump, by proportioning the sizes of the pipes and cylinders, but
means such as the hand valves, 5, or stops 54, will preferably be provided, by which
the operation may readily be adjusted, as described above.
In the organization just described, the force and suction valves are operated
directly by the pressure from the water cylinder on the opposite side of the pump.
The connections through which these valves are operated may be varied widely as to
form, without departing from this invention, and the valves operated may be the
main force and suction valves, as ordinarily applied, and as above described, or
auxiliary valves located anywhere 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, the same connections being used as above described.
In Figs 17, 18, and 19, is shown an organization in which auxiliary valves are
used on the force side, with a single cylinder on each side for applying the varying
pressure. The force chamber on each side of the pump is divided into two compart-
ments, one for each end of the plunger, and these compartments communicate by
ports 127 with the force main. These ports are controlled by means of disc valves
128, which are carried by a single valve rod 129, on each side of the pump, passing
through the wall of the force chamber, these rods being provided, at their outer ends
with pistons 107, which pistons move in cylinders 130, 131, on respectively the
leading and following sides of the pump.
The pressure from the water cylinders is transmitted to the cylinders 130, 131, on
the opposite sides of the pump, to actuate the pistons 107, and control the valves 128,
by the following means:-The water cylinder P on the leading side of the pump is
connected to the motor cylinder 131 on the following side by the pipes 132, 133,
these pipes entering the cylinder 131 on the opposite sides of the piston 107, and
connecting opposite ends of the water cylinder P with the corresponding ends of the
motor cylinder, so that the pressure transmitted through pipes 132, 133, respectively,
operates the piston in a direction to close the port 127 in advance of the plunger ()
on the following side, and to open the port behind the same at the moment when
that plunger completes its stroke in either direction. The water cylinder Q on the
following side of the pump is connected to the cylinder 130 on the leading side by
means of pipes 134, 135, these pipes, however, being so arranged as to connect
the ends of the water cylinder on the following side to the opposite ends of the
motor cylinder on the leading side, so that one set of connections are reversed,
as in the construction previously described.
While the pipes reversed in this construction are those connecting the water
cylinder on the following side to the motor cylinder on the opposite side, instead

page_text: of those from the water cylinder on the leading side to the motor cylinder on
the following side, as in the construction previously described, it is evident that the
result is the same in both cases, as an excess of pressure at one end of the
motor cylinder closes the valve at the opposite end of the water cylinder, so that the
pressure in front of the plunger on the leading side still is transmitted to the valves
at the diagonally opposite ends of the water cylinder on the following side, and
that on the following side to the valves at the corresponding ends of the cylinder
on the leading side.
It is evident that the operation of this construction is substantially the same
as that previously described, the reversal of the plunger on either side relieving the
pressure on one side of the motor piston 107 on the opposite side of the pump, and
transmitting pressure to the opposite side of the piston, the suction and force pressure
on one side of the pump being thus alternately transmitted to opposite sides of the
pistons 107 on the opposite side of the pump. In this case, the pressure behind the
plunger on one side of the pump is transmitted directly to one side of the motor
piston on the opposite side of the pump, and the pressure in front of the plunger is
similarly and simultaneously transmitted to the other side of the same piston. It is
apparent, therefore, that the piston is actuated in one direction or the other by the
difference between the pressures in front of and behind the plungers on the opposite
side of the pump. This, however, although less evident, is substantially the action
in the constructions previously described, employing the pipe 6 connecting the lower
ends of the motor cyclinders to the suction, as the pressure behind the plunger is
the same as that of the suction, and therefore the pistons are operated by the
difference between the pressures at opposite ends of the plunger. The only substantial
difference between the constructions is, that in this modification but a single
cylinder and piston is used for controlling all the valves on one side of the pump,
the pressure in front of the plunger being transmitted alternately to opposite sides
of the same piston, instead of to different motor cylinders and pistons, as in the
construction previously described. If, however, the pipes 6 are omitted, or open to
the air, the pressure in front of the plunger is opposed, not by the suction pressure,
as in the modification, but by the constant pressure of a single atmosphere.
While it is more desirable, for simplicity of construction, to place the auxiliary
valves shutting off the reaction of the water column upon the plunger beyond the
force valves, that is, between the force valves and force main, as shown in
Figs. 17 to 19, they may be located between the plunger and the force valves, and
operate as already described. Such an arrangement applied to the pump last
described is shown in Fig 20, in which the construction is the same as that shown
in Figs. 17 to 19, except that the auxiliary valves are placed inside of the force
valves, ports 136 opening from the water cylinders into the force chamber at opposite
ends of the plunger, and being controlled by slide valves 137 carried by valve rod 129
while the usual force valves k, l, open from the force chamber outside the auxiliary-
valves to the force main. A similar arrangement may be used on the suction side.
In the construction shown in Figs 17 to 20, it is obvious that if the voluntary
valves be omitted, the positively operated valves will be closed, so as to cut off the
pressure of the force main from in front of the plunger, and open the opposite end of
the cylinder to the force main, as the plunger reaches the end of its stroke, so that
these constructions may be used without the voluntary valves, provided that the
valve be operated just at the end of the stroke. It preferable, however, to use the
voluntary valves, so that the pump cylinder may be opened to the force main behind
the plunger, before the plunger reaches the end of its stroke, except as it is closed
by the voluntary valves, so that the valves may be closed in front of the plunger
gradually.
In Figs 21 and 22 is shown another organization in which auxiliary valves 128 are
closed by a constant pressure, controlled by a varying pressing. the constant pressure
being transmitted from the force main S to the upper sides of the pistons 2, through
pipes 139, and the pipes 119, 120, and 123, 124, from the respective pump cylinders
entering the motor cylinders below the pistons 2, The pipes 123, 124, from the

page_text: leading side of the pump, pass directly to the opposite side, and the pressure in the
ends of the pump cylinder Q on the leading side, controls the closing of the valves
at the corresponding ends of the plunger on the following side, while the pipes 119, 120,
from the pump cylinder P, on the following side, are reversed in crossing, and the
pressure in the ends of the pump cylinder P, on the following side, controls the
valves at the diagonally opposite ends of the plunger on the leading side.
It will be noted that the leading and following sides, in this construction, are
reversed from the constructions previously described.
In Fig. 23 is shown an organization in which constant pressure is applied to close
the valves, as just described, but is controlled by the varying pressure operating a
valve which admits the constant pressure to one side or the other of the pistor.
actuating the valves. This modification is shown as applied to the pumps shown in
Figs. 17 to 20, and previously described, but may be applied readily to other
constructions.
Referring to Fig. 23, the parts embodying the modification will be briefly
described. The construction on opposite sides of the pump being the same, and the
general arrangement of the pipes transmitting the varying pressure being unchanged,
only the leading side is shown, and a description of this will suffice.
The auxiliary valve rod 129, carrying the auxiliary valves 128, as in Fig. 17, is
provided at the end with a piston 140, moving in a cylinder 141, located on the side
of the force chamber, in a position similar to that of cylinder 130, the piston being
actuated in either direction by a constant pressure transmitted from the force main,
or other suitable source, through pipe 142, valve chamber 143, and the usual ports
opening to the opposite sides of the piston 140. These ports are controlled by a slide
valve 144, the valve rod of which is connected to a piston 145 working in a
cylinder 146 entered on opposite sides of the piston by pipes 134, 135, of Figs. 17
to 19, by which the pressure is transmitted from the water cylinder on the opposite
side of the engine.
The operation of this construction is exactly the same as that of the construction
shown in Figs. 17 to 19, except that the movement of the piston acted upon by the
varying pressure does not control the valve directly, but, through the slide valve 144,
controls the constant pressure and piston 140, so as to secure the closing of the
auxiliary valves 128 in the same manner as when they are directly operated by the
varying pressure.
This construction affords, also, a convenient arrangement in employing auxiliary
suction valves. As shown in this Fig. 23, the construction on the suction side is
exactly the same as that upon the force side, ports 127 connecting the suction main
and suction valves, and being controlled by auxiliary dise valves 148, carried by a
valve rod 149, which is connected to the piston 150, operating in a cylinder 151,
similar to cylinder 141 on the force side. The constant pressure may be transmitted
to the cylinder 151 on the suction side in any suitable manner, but the construction
shown will be found simple and efficient, in which pipes 152 connect the cylinders 141
and 151, so that the single valve 144 controls the admission of the constant pressure
to both cylinders on one side of the pump. As the force and suction valves, closed
simultaneously, are at opposite ends of the plunger, the valve rods 149 and 129 must
move in opposite directions, which result may readily be attained by crossing
pipes, 152, between the cylinders 141, 151, as shown, or in any other suitable manner.
While I have shown the pipes as connected directly to the body of the pump
cylinders, it is evident that they may connect anywhere between the plunger and the
inside valves on the force or suction side of the pump, as the pulsations of the fluid
are the same at any point inside of these valves. By the term " pump cylinder,"
therefore, intend to cover the entire space between the inner valves on the suction
and force sides of the plunger. It will be understood, also, that the term plunger
covers a piston.
In the constructions thus far described, the pressure within the pump cylinders
has in all cases been used as the varying pressure controlling the valves. It is
apparent, however, that the pressure behind the steam pistons varies in the same

page_text: manner as the pressure in front of the corresponding plungers. The pressure within
the steam cylinders, therefore, may be used in place of that within the water
cylinders, with substantially the sune results as described; such a modification is
shown in Fig. 24, in which the pipes transmitting the varying pressure connect, not
to the water cylinders at opposite ends of the plungers, but to the steam cylinders at
opposite ends of the steam piston; in this construction, the leading and following
sides are the same as in Figs. 21 and 22.
As the pressure behind the piston corresponds to that in front of the plunger, and
vice versa, it is evident that, as in the construction shown in Figs. 21, 22, a complete
reversal of the pipes forming the connections between the opposite sides of the pump
is necessary. The pipes 123, 124, therefore, from the opposite ends of the steam
cylinders on the leading side, pass to the valves at the corresponding ends of the
plunger on the following side, while the pipes 119, 120, from the following side, are
crossed, and pass to the valves at the opposite ends of the plunger on the leading
side. The pressure by which the valves are operated, however, corresponds in the
two constructions, the reversal of the arrangement of the pipes only off-setting the
reversal in the ends of the cylinders at which the operating pressure is found, and the
pressure behind the piston being only substituted for its equivalent the pressure in
front of the plunger.
It is evident that the pressure from the steam cylinders may be substituted, also,
for the pressure from the water cylinders in the other constructions shown, whether
the valves be operated by the varying pressure, or by an outside pressure controlled by
the varying pressure. Such constructions involve only corresponding modifications
in the arrangements of the pipes transmitting the pressure, and require no special
description or illustration.
It is apparent that many other changes might be made in the organizations shown,
without departing from this invention which is not to be limited to any of the special
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 those forms which are considered preferable. The broad invention, how-
ever, is of general application to pumps, independently of the special type of pump to
which it is applied.
By the term "duplex pump" used in some of the claims, it is meant and intended
to cover a pump having a plurality of plungers acting with each other, but with
their strokes timed differently, as, for instance, in the well-known Worthington
Duplex Pumping Engine shown herein, and other well-known pumping engines, and
it is not meant to include therein an engine having only a single plunger, or a
plurality of plungers connected so as to move in unison, as in the case of a single
double-acting pump.
By the term "constant pressure," it is not meant that the pressure tending to close
the valve is unvarying, as it is evident that this pressure will vary in the construction
shown with the changes in the pressure per square inch in the force main, and
variations in the "constant pressure" are immaterial, so long as it is in excess of the
pumping pressure, when the opposing varying pressure is reduced to secure the
closing of the valve against the pumping pressure.
Under the term "constant
pressure in excess of pumping pressure," is, therefore, included, any total pressure or
force of sufficient amount to close the valve against the pumping pressure, and so far
independent of the pump movement, as to require to be controlled by an opposing
varying pressure, to secure the proper valve movement.
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 method of controlling a pump valve, which consists in applying a fluid
pressure to the valve, and varying said fluid pressure during the stroke of the pump
plunger, to secure a closing pressure upon the valve, varying from a pressure below,
to a pressure in excess of the pumping pressure, substantially as described,

page_text: 2. The method of closing a pump valve, which consists in applying a fluid
pressure to said valve against the pumping pressure, and controlling said fluid
pressure to secure a closing pressure upon the valve in excess of the pumping
pressure, as the plunger reaches the end of its stroke, substantially as described.
3. The method of closing a pump valve, which consists in applying to said valve,
against the pumping pressure, a constant pressure in excess of the pumping pressure,
and controlling said constant pressure by an opposing fluid pressure, varying during
the stroke of a pump plunger, and reducing said opposing fluid pressure, to secure
the closing of the valve against the pumping pressure, by the constant pressure,
as the plunger reaches the end of its stroke, substantially as described.
4. The method of closing a pump valve which consists in applying to said valve,
against the pumping pressure, a constant pressure in excess of the pumping
pressure, and applying alternately, against said constant pressure, the suction and
force pressure of the pump, the suction pressure being applied to secure the closing
of the valve against the pumping pressure by the constant pressure, as the plunger
reaches the end of its stroke, substantially as described.
5. The combination with a pump valve, of a column of fluid having a pressure
varying during the stroke of the pump plunger applied to said valve, 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 column of fluid having a pressure in
excess of the pumping pressure, applied to close said valve against the pumping
pressure, substantially as described.
7. The combination with a pump valve subjected to a constant pressure against,
and in excess of the pumping pressure, of a column of fluid having a pressure
varying during the stroke of the pump plunger applied against said constant
pressure, substantially as described.
8. The combination with a pump valve, of a column of fluid having a pressure in
excess of the pumping pressure, applied against the pumping pressure, and a column
of fluid having a pressure varying during a stroke of the pump plunger, applied
against said constant pressure, substantially as described.
9. The combination with a pump valve subjected to a constant pressure, against
and in excess of the pumping pressure, of connections between said valve and a
source of fluid pressure in the pump, varying during the stroke of the pump
plunger, whereby a varying pressure is applied against the constant pressure,
substantially as described.
10. 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,
and means for controlling said pressure in accordance with the action of the plunger,
whereby the valve is closed against the pumping pressure, as the plunger reaches the
end of its stroke, substantially as described.
11. The combination with a pump valve, of a piston controlling said valve, and a
column of fluid having a pressure in excess of the pumping pressure applied to said
piston to close the valve against the pumping pressure, substantially as described.
12. The combination with a pump valve, of a piston controlling said valve, and a 4
column of fluid varying in pressure during the stroke of the pump plunger, applied
to said piston, to secure the closing of the valve against the pumping pressure, as
the plunger reaches the end of its stroke, substantially as described.
13. The combination with a pump valve opened by the pumping current, of a
piston controlling said valve, a column of fluid having a pressure in excess of the 5
pumping pressure applied to said piston, to close the valve against the pumping
pressure, and means for releasing said pressure, substantially as described.
14. The combination with a pump valve, of a notor piston controlling said valve,
and subjected to a constant pressure against, and in excess of the pumping pressure,
and connections between said piston and the pump cylinder, whereby the suction and 5
force pump pressures are applied alternately to said piston against the constant
pressure during the stroke of the pump plunger, substantially as described,

page_text: 15. In a duplex pump, the combination with a valve between the plunger and
force main, of a column of fluid from the opposite side of the pump, having a
pressure in excess of the pumping pressure, applied to said valve, against the
pumping pressure, as the plunger reaches the end of its, stroke substantially as
described.
16. The combination with a pump valve, of a piston controlling said valve, a source
of varying fluid pressure, connections between said piston and source of pressure,
and adjusting devices between the source of pressure and the valve, for varying the
time of action of the valve relatively to the variations in the pressure supply, to
secure the closing of the pump valve against the pumping pressure, as the plunger
reaches the end of its stroke, substantially as described.
17. In a duplex pump, the combination with a pump valve, of a column of fluid
from the opposite side of the pump, having a pressure varying during the stroke of
the pump plunger on the valve side of the pump applied to said valve, substantially
as described.
18. In a duplex pump, the combination with a pump valve between the plunger
and force main, of a column of fluid applied to said valve against the pumping
pressure, and means for controlling said pressure from the opposite side of the pump,
whereby the valve is closed in front of the plunger, as the latter reaches the end of
its stroke, substantially as described.
19. In a duplex pump, the combination with a pump valve subjected to a constant
pressure against, and in excess of the pumping pressure, of a column of fluid from
the opposite side of the pump, having a pressure varying during the stroke of the
pump plunger, applied against the constant pressure, substantially as described.
20. In a duplex pump, the combination with the pump valves, of columns of fluid
from each side of the pump, having a pressure varying during the stroke of the pump
plunger on the opposite side, applied to the valves on the opposite side of the pump,
substantially as described.
21. In a duplex pump, the combination with pump valves, of motor cylinders
controlling said valves, and connections between said motor cylinders and a source of
fluid pressure on the opposite side of the pump, varying during the stroke of the pump
plunger, whereby a varying fluid pressure on one side of the pump is transmitted to
the motor cylinders, and controls the valves on the opposite side of the pump,
substantially as described.
22. The combination with the pump cylinders, plungers, and pump valves, of a
duplex pump, of motor cylinders controlling said valves, and connections between
said motor cylinders and the pump cylinder on the opposite of the pump, whereby
the pressure in the pump cylinder on each side of the pump, is transmitted to the
motor cylinders, and controls the valves on the opposite sides of the pump,
substantially as described.
23. In a duplex pump, the combination of pump valves, motor pistons controlling
said valves, and subjected to a constant pressure against, and in excess of, the pumping
pressure, and connections between said pistons and a source of fluid pressure on the
opposite side of the pump, varying during the stroke of the pump plunger, whereby
pressure varying during the stroke of the pump plunger is applied to said pistons,
against the constant pressure, substantially as described.
24. The combination with the pump cylinders, pump valves, and plungers of a
duplex pump, motor pistons controlling said valves, and subjected to a constant
pressure against, and in excess of, the pumping pressure, and connections between
said pistons and the pump cylinder on the opposite side of the pump, whereby the
suction and force pressures in the pump cylinder on each side of the pump, are
alternately applied against the constant pressure on the opposite side of the pump,
and during the stroke of the pump plunger on the opposite side of the pump,
substantially as described.
25. The combination with the motor cylinders, their main and cut off valves, and
the pistons and plungers of a direct acting duplex pump, of valves between the
plungers and force main, columns of fluid having a pressure in excess of the pumping
C

page_text: pressure applied to close said valves against the pumping pressure, and means for
controlling said pressure from the opposite side of the pump, substantially as
described.
26. The combination with the motor cylinders, their main and cut-off valves, and
the pistons and plungers of a direct acting duplex pump, of valves between the
plungers and force main, subjected to a constant pressure against, and in excess of,
the pumping pressure, and connections between said valves and a source of varying
fluid pressure ou the opposite side of the pump, whereby the varying pressure is
applied against said constant pressure, substantially as described.
27. The combination with a pump valve, of a motor cylinder and piston controlling
said valve, and a hollow valve-stem opening into the valve chamber and the motor
cylinder, substantially as described.
28. The combination with a pump valve, of a motor cylinder and piston controlling
said valve, a hollow valve-stein opening into the valve chamber, and the motor
cylinder, and connections between the valve chamber on the opposite side of the
piston and a source of varying fluid pressure in the pump, substantially as described
Dated this 15th day of June 1897.
NEWTON & SON,
Agents for the Applicant.