Improvements in and relating to Direct-acting Steam Pumps.
Year: 1890

page_text: Date of Application, 21st Apr., 1890-Accepted, 5th July, 1890
COMPLETE SPECIFICATION.
Improvements in and relating to Direct-acting Steam Pumps.
I, DAVID GUELBAUM, of 127 Watt Street, Glasgow, Lanarkshire, Engineer, do
hereby declare the nature of my invention, and in what manner the same is to be
performed to be particularly described and ascertained in and by the following
Statement in writing, reference being had to the accompanying two Sheets of
Drawings, and to the letters and figures marked thereon, that is to say :—
The purpose or main object of my said Invention the working of direct-acting
steam pumps, with and to get the full advantage and economy of working the steam
expansively in their cylinders, by more simple and efficient construction and arrange-
ment of the cut-off and distributing steam valves, and mode of actuating the same.
Also new or improved constructions and arrangements of compensating water dis-
charge pressure vessels and pipes and of store air pressure chambers and air pump
and equivalent mechanical metal moving mass compensators, to enable such expansion
of the steam to be effected, and give an approximately regular delivery of the water,
notwithstanding the different steam pressures and motion of pistons caused by the
said expansion of the steam in the cylinders; and in the construction of other minor
details of the engines, all which will make these direct-acting steam engines moré
efficient and economical than they have been as heretofore constructed.
And in order that my said Invention and the manner of performing or carrying the
same into effect or practice may be properly understood, I have hereunto appended
two explanatory Sheets of Drawings, in which the same reference letters are used to
indicate corresponding parts in all the figures where shown. Figure 1 on Sheet 1
shows a sectional elevation through one cylinder A and its distributing and cut-off
steam valves a and b, ', of a double cylinder and pump arrangement of direct acting
steam pump, showing my improvements as applied thereto, and in which the rocking
valve gear shaft D of the one engine actuates the distributing valve a of the other
engine, but works the cut-off valves b, b, of its own engine. Figure 2 shows a
transverse section taken near the irregular line 1-1 in Figure 1, looking towards the
two pumps B, B, and showing one of the rocking valve lever shafts D in elevation in
its improved bush. bearings d, ds. Figure 3 shows a sectional plan and partial end
view, to a large scale, of one of the stuffing boxes c and fittings of the central screw
spindle for actuating the cut-off valves b, b, as seen in the general view Figure 1.
And Figure 4 is a sectional elevation of the air-pump II and its valve fittings to
show the details more clearly than can be seen in the small scale elevation in Figure 1.
Figure 5 is a transverse section of the discharge water forcing chambers B2, B2,
of the steam pumps B, B, shown in corresponding longitudinal section in Figure 6 on
Sheet 2, through one of the steam pumps B above the centre line, sufficient to show
the improvements connected therewith, and having the new store-air-pressure
chamber H secured to it over the centre. Figure 7 on Sheet 2, shows a sectional
elevation of the new separate air pressure regulating valve and water discharge
chamber E and connected main air-pressure chamber G; and Figure 8 is a sectional
plan of the said air pressure regulating valve and water, discharge chamber E.
Figure 9 shows a sectional side elevation of one arrangement of mechanical
compensator L or moving or rolling mass of metal to be used in connection with each
pump, instead of. the moving column of water and air pressure regulating and
discharge water chamber E shown in Figure 7. And Figure 10 shows an end
elevation at right angles to Figure 9 of the said compensators L, L, for both pumps
the one compensator L to the left being shown in section.. Figure 11 shows a side
elevation partly broken away of a somewhat different arrangement of the mechanical
pump compensator L from that shown in Figures 9 and 10, and actuated direct from
a continuation of the levers D¹ which move the valves of its cylinders.A.
Referring to Figures 1.to 3 of these Drawings, the Improvements of my Invention
Price 1

page_text: .
and mode of carrying the same into effect or practice consist all as follows
First, as regards the improvements connected with the expansion of the steam and the
cut-off valves, and mode of fitting and actuating these, either for working the steam
expansively in a single, or a duplex direct-acting steam pump, A2 is the piston rod
common to both the piston A! of the steam cylinder, A, and that B' of its pump B for
each engine, and the cylinder and pump are connected at their adjacent ends by the
usual cradle C for each engine, and each steam cylinder is formed with an inlet and
exhaust port a, a, leading from near its. ends to the working face of its slide
distributing inlet and exhaust valve a, formed with an exhaust port and chamber in
the centre leading to the exhaust chamber and pipe all in the cylinder face between
the ports a, a Near the ends of the slide valve a inlet ports and passages a². a²,
are formed through it which has a working face on the back with cut-off steam
valves bbworking over these faces and ports for admitting the steam from the
casing A³ to the cylinder A and cutting it off, according as the cut-off valves b, b, are
set; and each slide valve a and its spindle of double cylinder engines is actuated
through a link rod a³ from the rocking or wiper shaft D and lever D¹, of the
opposite engine by its piston rod A, all so far substantially in a usual manner.
in
My Improvements as applied thereto consist in mounting the two plate cut-off
valves b, 1, (such as are used in ordinary engines) on the back of the slide valve a,
of each direct-acting pumping engine, and in connecting one valve by a right
handed screw to its actuating centre or solid spindle 2 and the other valve b¹ by a
left handed screw formed on a tubular or sleeve spindle 11, mounted and fitted to
turn on the central spindle 2 of the other valve, or vice versa the left handed screw
might be on the central spindle and the right handed screw on the hollow spindle.
These spindles 26" work steam-tight out through stuffing boxes c, c, at opposite
ends of the steam casing A3, with grooves and feathers 63, 6111, at their outer ends,
connecting them to hexagonal or other turning wheels or bushes & mounted in the
outer end of the stuffing boxes c, c, and retained in position by outer plates as seen
more particularly in the enlarged views Figure 3. The turning of these bushes
one direction or the other by a screw key or otherwise, thus turns their respective
spindles 3, 1, and shifts the cut-off plate valves b or to or from each other, to give
any desired cut-off or expansion of steam; and to show the position of these valves
on the outside, a small elastic band of steel, or it might be a chain c', is mounted on
a barrel part of each turning bush 4, working out through a slit in the stuffing
box c, having its other end wound round a small spring wheel or pulley c² mounted
to turn loose on a lateral stud c¹¹ projecting out from the ends of the cover A* of the
steam casing A³ as seen more particularly in Figure 1 ; and divisions and numbers
would be engraved or stamped on these spring bands or chains c¹ which would show
the number of turns taken in one direction or the other, by the bushes b, and their
respective spindles 3, 6, and thus show the position of the cut-off valves b, b₁,.
respectively by examining the position of the bands or chains in relation to some fixed
index or point on each stuffing box c, for giving any desired length of stroke cut-off
and expansion of steam by the valve b, b, within the casing. As these cut-off
valves are reciprocated in the opposite direction to their slide valve a, their
spindles, are connected by a joint head d and link d¹, to a short arm or
lever d formed or secured on the levers D₁ of the rocking spindles D to act in
the reverse direction to these levers D¹, which are actuated by the links D" from
the blocks D2 secured to the piston rods A. As shown in Figure 2, these rocking
lever spindles D for actuating the valves, are here shown as mounted in a strong
bracket C, projecting up from and bolted by flanges at C" to the upper edges of the
two cradles C, each formed with a new or improved tapered or conical journal d² at
opposite ends, with conoidal bushes d³ fitting these journals d' and turned cylindrically
on the outside to fit a bored part at each end of the bracket (³, with a screw
nut fitted on the outer projecting ends of the bushes d³ and each fitted with a
slot d' on the upper side and fitted with pinching screws and jam nuts d³ through
the bored ends of the bracket C₁ to take into the slots d' and so hold the bush in its
- tightened up position, and also prevent it being turned round while the bush is being

page_text: tightened up against the tapered journal d by the nut d¹¹ acting against the eye of
the lever D', and which when the bush was tightened up and secured by the pinching
screw d³, could be slackened back to prevent friction on the eye of the lever Dr.
Referring to Figures 5 and 6 on Sheets 1 and 2 respectively of the Drawings, a
further improvement consists in fitting each pump B, with a separate discharge water
forcing chamber and vessel B2, by a longitudinal division partition B", (instead of as
usual in duplex direct-acting pumps making one discharge chamber do for both
pumps) with a discharge branch B³ leading from cach chamber B2 by long pipes Bill
both led to the inlet branches E' of a new single separate water air pressure forcing
vessel E with air pressure regulating valve Ff and float F shown in Figures 7
and S, and with only one discharge forcing pipe E², the arrows in these Figures 5
to 8, indicating the flow of the liquid. The top or cover E³ of this water forcing
vessel E is fitted with an air chamber e connected by a pipe G¹ to the top of a large
main air pressure chamber G, and the cover E³ is fitted in the centre of the air
chamber e with a vertical valve chest F, in which is fitted and mounted a central
cylindrical hollow equilibrium valve f open at both ends, and having its spindle f¹
continued down through a guide screw bush F, in the lower end of the valve
chest F, and secured by a screw and washers at its lower end 11 to the bottom of a
hollow cylindrical float F2, guided and reciprocating vertically in the upper part of
the water vessel E to regulate the displacement of the water therefrom through the
pipe E according to the pressures of the air in the upper part of the vessel E.
This water pressure forcing vessel E and main air pressure vessel G are both placed
in the ground or otherwise at a considerable distance from the pump B, and the
upper valve chest F is formed with an annular recess, round the valve and fitted
with an air branch and tube fled away and connected at f³ to the upper part of the
new store air pressure chamber H, screwed to the upper part of the case of the
discharge water pressure chambers B2 as seen particularly in Figure 6. The lower
part of this valve chamber F is formed with a series of holes e' leading to and from
the air chamber e, and main air pressure chamber G, and this air chamber e is fitted and
connected by an air branch and tube e and led away to a gauge eat the upper part
of the air pressure chamber H, the pressure within this chamber H being indicated by
another gauge. This store air pressure chamber H, as shown in Figure 6, is preferably
made conoidal, and secured at its lower apex end by a screw coupling piece H¹ to the
centre of the upper part of the discharge water chests B2 of the pumps, and fitted with
a cup leather at H" covered with oil to prevent the escape of the pressure air. This
chamber His fitted in the upper central part with an escape air pressure loaded
valve H2, screwed to the upper end of a cruciform spindle H3 shown in section at
Figure 6 A, having mounted on it a pressure spiral spring H, regulated to the desired
pressure by a screw and nut above the valve H2. The air is forced into this store
pressure air chamber H by the pipes and a special plunger air-pump I, I', shown in
elevation in Figure 1, bolted at 1 to the upper edges of the two cradles C close to
the pumps B, B, and having the plunger 1 actuated by a gab link I from a
lateral pin in one of the valve levers D'. This air pump barrel and chamber 1 as
shown in enlarged sectional elevation in Figure 4, is worked preferably with oil to
give a small regulated clearance and high pressures of air, and having a part at I² of
its inlet and discharge chamber always filled with air under the cover I³ to which is
fitted an inlet spring valve within an enclosing protecting chamber fitted with inlet
air holes near its lower edge, and with a pinching screw for keeping the valve i
open and stopping the action of the pump without disengaging its working rod I
This pump I, I, is also fitted with a screw I in its back end, for screwing more or less
to regulate the displacement of oil at each stroke and clearance for air under the
valves i, j, above. A discharge air valve is also fitted in the cover I³ within a
discharge chest, formed and fitted with a discharge branch and coupling of the
air tube ja led and jointed to a coupling branch at at the lower part of the new
store air pressure chamber H, the direction of the air currents being all as indicated
by the arrows in Figures 1, 4, 6 and 7.
The action of the air apparatus in connection with the store and main air chambers,

page_text: h
is as follows. Supposing the quantity of pressure air within the distant main air
clamber G is sufficient in so much that the water level within the air forcing vessel 5
is below the float F which consists preferably of wood covered with india-rubber,
then the latter, not being supported by the water, will by its weight draw down the
piston valve and shut up the annular recess leading to the tube 2 and thus separate
the main air chamber G from the store pressure air chamber H in which-as
mentioned the pressure by means of the air pump I and indicated by the gauge
is brought to a certain degree higher than the pressure within the main air chambers G
and E, the pressure within which is indicated by the gauge near the pump.
While this takes place, that is, while the water level within the air apparatus E is
below the float F, the gauge of the store air pressure chamber H will show a high
and constant pressure (the air pump I being kept at rest), while the gauge ³ of the
distant main air chamber Ġ will show a lower and variable pressure on its index e³,
its pointer having an oscillatory motion as usually the pressure within the air
chamber E is periodically falling and rising during the working of the water
pumps B, B. Such a state of the two gauges serves as a signal for the machinist
that the things are going all right. As soon, as the water level within the air forcing
apparatus, E in consequence of loss of pressure in the main air vessel G raises the
float the valve will be brought by the latter into the position shown in Figure 7
and the main air chamber G will be brought-for a moment only-in communication
with the store air pressure chamber H from which a stream of high compressed air
will come by the pipe into the air and water forcing apparatus E and lower its
water level and float F, and thus disconnect this chamber E and air vessel G from
the store pressure air vessel H. This state of things will go on until the pressure
within the store air chamber H gets nearly equal to that of the main air chamber G.
Both then will remain in constant communication, and their gauges and e³
respectively will show nearly the same oscillating pressure, which will serve as a
signal for the machinist as to the want of air in the distant main air chamber G.
Then if the air pump I be put to work by connecting its gab rod 11 to the moving
lever D¹ of the engine, it will introduce by the pipe fresh pressure air into the
store chamber H and main air chamber G (both being in communication with each
other) each time the float F2 rises, until the water level within the air forcing
apparatus E falls below the float F2, and the main air chamber G gets disconnected
with the store air chamber H and the gauge h of the latter will show a pressure
greater than that shown by the gauge e of the main air chamber G. The air
pump I can again be stopped, and the operations go on as before. It is evident,
that the greater the volume of the store air pressure chamber H and the higher its
pressure is kept, the seldomer will the machinist have to use the air pump; it is
also clear, that the piston valve f need not bo quite close to its cylinder F, no loss
of air being caused by having a small clearance; and thus the pressure within the
distant main air chamber G can be perfectly controlled by the machinist as described
from looking at the indices and e³. The advantages of such a well governed
distant air chamber G and of the complete isolation of each pump B and its forcing
chamber B from that of the other pump, is as follows:-The volume of the
distant main air chamber G being sufficiently large its pressure will vary very little
during the piston stroke, and, therefore, can be considered as a constant pressure,
nearly equal to the pressure in the vessel E, due to the height of the forcing
column in the discharge pipe E2, with some slight pressure additional caused by the
friction along these pipes E2: By this pressure the water columns in the pipes B
between each pump B and the air pressure regulating vessel E and G will be kept
close to its piston 'B' to form a solid mass. On this mass the steam during the stroke
will act immediately against nearly a constant resistance (caused; as said, by the
presence of the large distant air chamber G) with full pressure higher than this
resistance at the beginning of the stroke, and at the end of the stroke with a pressure
lower than this resistance caused by the expansion of the steam. The result of such
an action of the moving power-as known by the mechanic-will be :-(1st) The
velocity of the piston together with its connected water column; during the full

page_text: pressure of the steam will be far less, than in the case when the air chamber is put,
as usual near the pump, and only the piston alone is submitted to the immediate
action of the steam, because, the greater the mass on which the power is acting, the
less is the velocity operated by this power during a certain time. This circumstance
gives the possibility to use steam of much higher pressure, than that used in pumps
working without steam expansion, without increasing the ordinary average piston
velocity. (2nd) The surplus of work developed by the steam towards the work of
the resistance, during the first half of the stroke, will be transformed in vis viva of
the moving water column in the pipes B and delivered again during the second
half of the stroke by the inertitude of this mass, thus the motion of the piston will
continue even after the falling of the steam pressure, and at each end of the stroke
a due volume of water will be brought into the air apparatus E with a desired
average velocity independently of the unequability of the moving power during the
stroke. In this way the moving power is compensated and the motion uniformly
conserved by means of the pumped water itself, without the introduction of a foreign
mass or resistance.
Another mode of compensating for this differential pressure and action of the steam
and water pistons by using the steam expansively during the stroke as shown in
Figures 9 and 10, consists in the use of a cylindrical moving or rolling mass coupled
to each piston rod A³. This metallic mass consists of a compact cylinder L, the
exterior diameter and length of which can be made as large, as it is found convenient.
This cylinder L is coupled at its centre L' to the piston rod A2 by a hand engaging
gab link L for which there is made in the cylinder La suitable segmental groove L".
Besides this groove L" there are made two other segmental recesses L (shown
in dotted lines) at a certain smaller radial distance (r) from the centre L' than the
radius (R) of the whole mass for rolling on the supporting guides L³ projecting up into
the segmental grooves I being both (the recess and the guides) easily formed with
teeth on their contact surfaces to insure the rolling action of the mass on the guides L³.
Thus, the metallic mass L by the straight motion of the piston rod L and its connect-
ing link I will get a rotative motion about its axis on the supporting guide I³,
with a velocity at its circumference
(✗HI) greater than the velocity of the piston.
This circumstance-as can be clearly proved theoretically-does so much increase the
vis-viva of the moving metallic mass L that, for the case illustrated at Figures 9
and 10 of the Drawings, the action of such a metallic mass, weighing only say half a
ton, is equal to the action of a length of nearly four hundred feet of a water column
in the tubes B1 between the pumps B and the pressure regulating apparatus E. By
adding to or taking off the discs or plates 1, 1, at the sides of the mass the average
piston velocity can be increased or diminished without any other change in the action
of the pumps. By the introduction of such a metallic compensator, the forcing air
chambers can he arranged as usual and the hereinbefore described new store and distant
air chambers H and G with the air apparatus E can be dispensed with or such a
metallic mass can be used in combination with the said air vessels and pressure regu-
lating apparatus by diminishing the length of the moving column between these
apparatus and the pump, with a less weight of moving mass, both arrangements com-
pensating for a mean proportion of the difference of power exerted in the cylinder by
the expansion of the steam during each stroke. These metallic compensators L can
also be placed between the steam cylinder A and its pump B below their common
pistion rod A' so as to be actuated as described and thus little extra room will be
required for the working of these compensating rolling. masses. Thus it will be seen
each metallic mass can be easily connected or disconnected with the piston rod A*
while the latter is in motion by its gab link L. Figure 11 shows a modified arrange-
ment of moving and coupling the rolling mass L from that shown in Figures 9 and 10,
by its gab link L' connected to a pin in a continuation D³ of one of the levers Di
which works the valves actuated by the piston rod A³, but otherwise substantially the
same as described in reference to Figures 9 and 10.

page_text: Having now particularly described and ascertained the nature of my said inven-
tion; and in what manner the same is to be performed I declare that what I
claim is
First. The construction, or arrangement and combination of the parts of single and
duplex direct-acting steam pumps, with their steam distributing cut-off expansion
valves and cut off regulating and indicating mechanisms, and store and air pressure
chamber and air pump and distant main air pressure vessel, and pressure regulating
liquid vessel with valve and float, and range of water pipes between these and the
pumps, and with air pressure indicators, all substantially as and for the purposes herein
described in reference to and shown in the accompanying Drawings.
Second. In direct-acting steam-pumps, the arrangement and use of steam dis-
tributing cut-off expansion valves operated by the lever mechanism of the distributing
steam slide valves in combination with the mode of setting these by duplex screw
spindles and their turning wheels, with means for regulating and knowing the position
of the valves on the outside, all substantially as herein described in reference to
and shown in the accompanying Drawings.
Third. In direct-acting steain pumps, the constructing. of the journals and tighten-
ing-up bushes of conoidal shape for the valve rocking shafts, substantially as herein
described in reference to and shown in the accompanying Drawings.
Fourth. In direct-acting steam pumps, the combination and use of force and
distant air-pressure water chambers with pipes and water column moving mass
between these, and with store air-pressure chamber and pump, and main distant air-
pressure chamber and liquid-pressure vessel with regulating valve and float, and either
with or without an equivalent vis viva rocking metal mass, all substantially as and
for the purposes herein described in reference to, and shown in the accompanying
Drawings.
Fifth. In direct-acting steam pumps working expansively, the use of a mechanical
rolling mass for taking up the vis viva at the early part of the stroke, and giving it
out at the latter part of the stroke, substantially as herein described in reference to and
shown in the accompanying Drawings.
Sixth. In direct-acting steam pumps, the use of an air pump in combination with
a store air-pressure chamber, substantially as and for the purposes herein described in
reference to and shown in the accompanying Drawings.
Seventh. In direct-acting steam pumps, the combination and use of a store air-
pressure vessel with a main air-pressure chamber and air and water pressure apparatus
with regulating valve and float, substantially as and for the purposes herein described
in reference to and shown in the accompanying Drawings.
Eighth. In direct-acting steam pumps the combination and use of an air and water
pressure apparatus with regulating valve and float placed between the force discharge
water pressure chamber, and the distant main air pressure chamber, substantially
as and for the purposes herein described in reference to, and shown in the accompanying
Drawings.
Ninth. In duplex direct-acting steam pumps, the use of separate water forcing
chambers, with column pipes leading to the distant air-pressure regulating and com-
pensating vessels, substantially as and for the purposes herein described in reference to
and shown in the accompanying Drawings.
1011
W. R. M. THOMSON & Co.,
96, Buchanan Street, Glasgow, Agents.