Improvements in Direct-acting Pumping Engines.
Year: 1899

page_text: Date of Application, 19th Dec., 1899-Accepted, 17th Feb., 1900
COMPLETE SPECIFICATION.
Improvements in Direct-acting Pumping Engines.
I, HARMANUS LANSING PERRINE, of P.O. Box, No. 5, Milwaukee, County of
Milwaukee, State of Wisconsin, United States of America, Mechanical Engineer,
do hereby declare that 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 invention herein is directed to improvements in twin vertical air-pumps
wherein two high or a high and a low pressure steam cylinder is employed with a
working-beam and my said improvements consist of certain parts and combina-
tions of parts in which the working-beam, valve-gear and slide-valve co-operate
for controlling two steam pistons of duplex steam-ends in a way and by means
which I shall particularly point out in the claims concluding this specification.
In the accompanying drawings I have shown a pumping engine embodying my
invention in the form at present preferred by me and of which the following is a
description; but it will be understood that various modifications and changes of
details may be made without departing from the spirit of my invention and
without exceeding the scope of the claims.
In these drawings:
Figure 1 shows in front elevation compound steam-ends as applied to a vertical
twin air-pump in which the valve mechanism is operated and controlled from
the working-beam in accordance with my improvements;
Figure 2 shows an end view of the compound-levers of the valve-gear;
Figure 3 shows enlarged the compound steam-ends, the valve-gear and its
connection with the steam-chest, the cover of which is removed to expose the
main and auxiliary slide-valves, the cylinder of the reversing piston being in
section--and the piston in position ready to reverse the stroke of the steam
pistons;
Figure 4 is a vertical section taken through the steam-chest, the main and
auxiliary slide-valves, the high pressure cylinder being removed to show the high
pressure ports in the port-casting;
Figure 5 is a vertical cross section of the port-casting taken on the line 1-2
of Fig. 6, showing the relation of the ports for both the high and the low pressure
cylinders;
Figure 6 is a horizontal section of the port-casting and steam-chest showing
the double ported slide-valve in position when about to reverse the stroke, and
showing the relation of these parts to the high and low pressure cylinders;
Figure 7 is a view like Figure 3 showing a double slide-valve for controlling
two high pressure cylinders, the steam-chest and slide-valve partly cut away
to show the port-casting with valve-face and the steam and exhaust ports for each
cylinder;
Figure 8 is a plan view of Figure 7, the port-casting, slide-valve and steam-
chest partly in section;
Figure shows in elevation a modified construction of the valve-face and

page_text: port-casting whereby trunk or differential pistons are used with live steam only
on the up stroke; and
Figure 10 is a plan view of the same showing the port-casting and slide-valve
partly in section, the ports and the relation thereto of the slide-valve for reversing
and exhausting the steam pressure from the lower to the upper side of the
piston.
Referring to the drawings the steam-ends and valve-gear are shown as applied
to air-pumps which may be of any well known construction; but my new
combination may be applied to a plunger or piston water-pump, or air-compressor.
A port-casting of novel construction connects the two steam cylinders and
forms a face for the steam-chest, valve, valve-seat and ports in connection with
the slide-valve; while the valve-gear in its connections with the slide-valve
and the reversing piston also constitute a feature of my improvement.
slide-
In Figs. 1, 3 and 6 are shown the vertical twin steam-cylinders as connected
by the ported-casting, and in such construction the well known "Allen
valve is used for admitting and exhausting steam to and from the compound-
cylinders.
In Figs. 4, 5 and 6 it is better seen how the ports cross to the high pressure
cylinder X which may be twelve inches in diameter; and the low pressure
cylinder Z which may be twenty inches in diameter, being about three ratios
to one, so that the steam used in the high pressure cylinder will be expanded
to and exhausted from the low pressure cylinder.
In Fig. 1 the position seen in dotted lines of the piston in the low pressure
cylinder is at the top of its stroke and the piston of the high pressure cylinder
seen in dotted lines is at the bottom thereof, both pistons being connected to
and actuated by the beam A which is suitably mounted in the frame. These
cylinders are connected by a ported-casting B, so that a center line drawn through
said casting will intersect the centers lengthwise of the vertical cylinders;
while the steam-chest Q is mounted upon one side of the ported-casting. This
construction gives a convenient arrangement of the cross position of the ports
that is necessary for admitting and exhausting steam from the cylinders and is
shown in Figs. 3, and 6. It also gives a convenient arrangement of the
steam-chest and its valves and valve-gear for controlling said parts.
The ported-casting for this purpose has port-faces at three of its sides two
of which M and N Figs. 5 and 6 join the port sides of the steam cylinders; the
third ported side forms the valve-face or seat P Figs. 6, 8, 9 and 10. It carries
the steam-chest Q and reversing cylinder as seen in Fig. 3, and its fourth side is
flanged for the exhaust pipe at I Figs. 6 and 10...
The steam cylinders are mounted upon a suitable supporting frame at the end
of which next the high pressure cylinder is mounted the compound-levers and
connections of the valve-gearing while mediately of the cylinders and below
the frame-entabliture is mounted the working-beam.
The relation of the ported-casting to the cylinders brings its valve-face or
seat P Fig. 6 to the front so that the steam-chest will occupy a position in front
of and between the cylinders, so that the compound-levers and valve connections
will be located at the side of the high pressure cylinder.
A strong bracket casting C bolted to the front side of the entabliture forms
the pivot-bearing f of an upward standing lever F, the upper end of which is
connected with the auxiliary piston.
In bearings e on this lever near its pivoted end is mounted a horizontal rock-
shaft d on the inner end of which is an upward standing short crank-arm c
Figs. 1, 2 and 3 to which the main valve-rod h is connected by a link i.
To the outer end of the rock-shaft is keyed a downward standing lever E which
is connected to the working-beam by a crank R on the shaft thereof and a link y
which is made adjustable.
The rod h which connects the lever E is screwed into the yoke J and carries
the main slide-valve D, and on the upper side of this yoke is placed the auxiliary

page_text: slide-valve H which controls the valve driving piston G Fig. 3. This auxiliary
valve H has a continuous motion co-incident with the main pistons.
The main slide-valve D) moves only twice the width of the steam-ports --
Figs. 3 and 6, while the travel of the valve-rod h, the yoke J and the auxiliary
valve His four times the width of the ports thereby necessitating a lost motion
between the yoke and main valve of twice the width of the ports.
The cylinder K of the auxiliary or reversing piston is preferably cast integral
with and on the top and long side of the steam-chest and has double ports k
Fig. 3 for steam and exhaust so that a cushion-valve M3 Figs. 1 and 3 may be
used to cushion the driving or reversing piston G which is connected to the
lever F through the link 1, whereby the main slide-valve is moved to a position
of wide open after it has been moved to line and line through connections from
the working-beam as shown in Figs. 3 and 6.
Reterring to Figs. 1, 3 and 6 No. 1 illustrates by dotted lines the piston
movement of the low pressure cylinder and No. 2 the relative piston movement
of the high pressure cylinder, and in the positions of these pistons and their
controlling valves, steam is being admitted to a port a under the high pressure
piston at the same time the exhaust from the upper side of the piston is exhaust-
ing through port a¹ and double ported valve 1 into the low pressure valve port a³
to the upper side of the low pressure piston for the down stroke; while in the
mean time the exhaust passes out of the low pressure port into the main
exhaust S. This action is reversed by the beam and the auxiliary piston G,
the admission ports - and the exhaust ports - Fig. 3 being seen in full
and dotted lines with the auxiliary piston in position just ready to reverse the
stroke of the steam pistons, and carry the main valve across the ports to wide
open.
The location of the ported-casting having the construction described with
respect to the twin cylinders is an important feature of my improvement because
it gives a very advantageous arrangement for the auxiliary piston and for the
steam-chest by reason of making all the movable joint connections of the valve-
gear much more direct, compact and shorter and as a result thereby reducing
the extent of condensing surface, and because it provides single ports for admis-
sion and for exhaust instead of the common practice of using double ports,
thereby making an appreciable saving in the volume of steam used. By placing
the chest and the reversing piston in a horizontal position a bearings Figs. 3
and 4 is provided on the lower side of the chest for supporting the main slide-
valve and insuring its seating against the main port-face.
At the upper side of the chest is provided a ported seat for the auxiliary valve H
Fig. 3 which controls the reversing piston. This valve is carried on the valve-
rod yoke in an inverted position whereby all water of condensation will be
drained from the reversing cylinder and a thorough lubrication of the valves
insured.
In the employment of the double ported slide-valve for both high and low
pressure cylinders a very direct communication for both admission and exhaust
is provided and this ensures an even and uniform motion to both pistons through-
out the stroke.
Looking at Figs. 3, 6, and 7 the main valve has been moved to the left to a
position of line and line with the ports by direct action through the compound-
levers and their connection with the beam.
A slight lead is given to the auxiliary valve H so that live steam is admitted
behind the reversing piston which is driven to the left and through the rod
moves the lever F carrying with it the rock-shaft 7, its crank-arm and lever E
and thereby through the link i and valve-rod and yoke J, move the main slide-
valve D to its extreme travel across the ports to wide open and reversing the
stroke of the main piston.
A by-pass port is provided for admitting live steam to the low pressure
cylinder when starting through the slide-valve as in Figs. 4 and G. -

page_text: Figures 7 and 8 illustrate the application of the compound or differential
lever-valve gear as applied to a double D valve driving two simple high pressure
pistons of equal diameter and stroke. In Figs. 7 and 8 this double D valve controls
the admission and exhaust from each cylinder through single steam ports s—s¹—
and out into a common exhaust port t.
The three faced intermediate casting connecting the steam cylinders at the
faces MN, has two common three ported valve faces or seats on the third or
chest side, these ports are covered each by two common D valves cast together
and are moved or operated by the gearing as one plain slide-valve admitting and
exhausting from each cylinder as in a separate engine.
The steam pistons travel in opposite directions and cross in the center of the
stroke.
In Fig. the valve seat of cylinder No. 1 is shown with the steam ports of
cylinder No. 2 in dotted lines, the chest cover being removed to show the slide-
valve D', yoke J and the auxiliary valve H in the position of admitting steam to
the pistons.
The main slide-valve is at line and line moving to the left reversing the stroke
of the pistons, live steam being admitted at 1 Fig. 8 for the up stroke of No. 2
and at Figs. 7 and 8 for the down stroke of No. while the exhaust is through
ports and Figs. 7 and 8.
S
Figures 9 and 10 illustrate the application of the same double slide valve D¹
as applied to driving the trunk or differential pistons,--live steam being used
only for the up stroke of each piston and expanded from under to upper end of
each piston alternately. In this arrangement the steam ports are placed side
by side with the exhaust t in the center and between the initial port of each
cylinder.
The steam supply connection is made at T; and the slide-valve is operated
as above described.
In the position of the slide-valve D¹ seen in Fig. 10 its cavities and V2 are
at line and line with the ports, moving to the left ready to admit live steam to
the under side of the trunk piston No. 2 and exhausting from the upper side
through port into port t and to the condenser.
Piston No. 1 having completed its up stroke the steam is expanded from the
under to the upper side of the piston through the exhaust cavity V2 of the slide-
valve and doing work on the down stroke due to the difference in diameter of
the trunk and piston.
It will be seen that live steam is admitted from the chest only through the
ports Fig. 10 leading to the under or trunk side of the pistons for the up
stroke.
Looking at Figs, 8 and 10 n indicates the port leading to the top of No. 2 and
the port leading to the bottom thereof; while ² indicates the port leading to
the bottom of No. 1 and 3 the port leading to the top thereof.
T is the main steam inlet.
I have described and claimed the port casting as a separate part or element
when fitted and uniting two steam cylinders side by side which will be the
method of construction where the same steam cylinders are to be used for
different spreads or centers, driving larger or smaller size pumps.
It may be advisable however in making standard patterns for fixed centers to
mold the two steam cylinders and their ports and valve-seat, all in one casting
which can be done in a three part flask and without departing from my invention.
Having now particularly described and ascertained the nature of my said
invention and in what manner the same is to be performed, I declare that what
1 claim is:-
1. In a duplex pumping engine and in combination with separate steam
cylinders and their pistons, a casting between and joining said cylinders with
ported faces, and having an intermediate third ported face, the ports whereof

page_text: communicate with said cylinders, a steam-chest on said third ported face, a
main slide-valve controlling said intermediate ported face, a reversing piston on
said chest, an auxiliary slide-valve actuated by the said main slide-valve rod or
yoke, a working-beam connected to the main slide-valve and with the reversing
piston for operating the same, whereby both main and auxiliary slide-valves are
caused to have direct and coincident movements with the main pistons.
2. In a duplex pumping engine and in combination with the steam cylinders
and their pistons, a casting between the cylinders having three ported-faces, two
of which join the cylinders, a steam-chest on the third ported face, a double ported
main slide-valve on said chest face, a ported cylinder on the long end of said
chest, an auxiliary valve at said long chest and actuated by the main slide-valve
rod or yoke, a reversing piston for said cylinder, the working-beam and means
for connecting it with the rod of the main and auxiliary slide-valves, and the
reversing piston for effecting their direct and coincident movements.
3. In a duplex pumping engine and in combination with the steam cylinders
and their pistons, a casting between the cylinders joining them with ported-
faces and having an intermediate main valve-seat, a steam-chest covering said
main valve-seat and having a side seat on its long end forming part of said chest,
a double ported main slide-valve for the intermediate seat and an auxiliary
single ported slide-valve for said side seat, actuated by said main slide-valve rod
or yoke, an auxiliary cylinder for said side ported seat, a reversing piston at
the ported side seat, and means connecting the main and auxiliary slide-valves
and the reversing piston consisting of the working-beam, the lever E directly
connecting the beam and the double ported slide-valve, the lever F having the
fulcrum for the lever E and connecting the reversing piston, substantially as
described.
4. In a duplex engine and in combination with the steam cylinders and
their pistons, a casting between and joining the cylinders with communicating
ported faces on a line intersecting the centers of said cylinders, and having an
intermediate double ported seat, a steam-chest covering said seat and having a
side seat at its long end, a double ported slide-valve for the intermediate seat
and a single ported slide-valve for the side seat actuated by said main slide-valve
rod or yoke, a ported cylinder on the long end of said chest, a reversing piston,
a working-beam and a pair of levers standing in opposite directions, one directly
connecting the beam and the double ported slide-valve, the other connecting the
piston of the reversing cylinder, both levers pivoted together for actuating the
main and the auxiliary slide-valve and the reversing piston with coincident
movements.
5. In a duplex pumping engine and in combination with twin high pressure
steam cylinders and their pistons having equal diameter and stroke, a casting
between and joining said cylinders with ported-faces in communication there-
with, a steam-chest on the third ported face, a reversing piston in said chest, a
slide-valve comprising two D valves in one, an auxiliary slide-valve and
mechanism connecting the double slide valve, the auxiliary slide-valve and
reversing piston for operation as described.
HOW
+
1000
SYDNEY E. PAGE,
28, New Bridge Street, London, E.C., Agent for the Applicant.