Year: 1885

page_text: I WILLIAM DONALDSON, Mechanical Engineer, of Leathwaite, Ambleside, in the
County of Westmoreland, do hereby declare the nature of this invention, to be
as follows:-
This invention relates to the use of fluids of any kind, either liquids or gases,
under any assigned pressure, for pumping fluids of any kind either liquids or
gases under the same or under any other pressure different from the pressure of
the motive fluid.
The valve, which admits the motive fluid into the motive piston cylinder and
allows it to escape at the completion of the stroke, is automatic, loose, and totally
disconnected from any other moving part of the machinery and is actuated solely
by the alternate admission of the motive fluid whilst under the maximum working
pressure at the end of the working stroke, through an inlet port-hole leading from
the motive cylinder into the valve chamber, and the exhausting of the fluid, so
admitted, at the end of the return stroke, through an exhaust port-hole. The rate
of working of the pump varies automatically with the quantity of fluid to be
pumped in any assigned time. The invention is fully described as follows,
reference being made to the accompanying drawings in which like letters describe
like parts.
Fig. 1 is a sectional elevation through the centre of the pump barrel, outlet and
inlet, valve chambers and inlet valve for admitting liquid exhausted from
automatic valve chambers and also leakage liquid into pump barrel; Fig. 2 a
sectional elevation at right angles to the section Fig. 1 through pump barrel, part
of motive cylinder, and through port-holes situated between valve cylinder and
motive cylinder; Fig. 3 a sectional elevation, likewise at right angles to section
Fig. 1, through centre of valve chamber; Fig. 4 a transverse section through
motive cylinder and piston below the exhaust port from the valve chamber;
Fig. 5 a transverse section through the inlet port of the valve chamber; Fig. 6 a
transverse section through the port B₁; Fig. 7 a transverse section through the
port B³
The alternate admission and exhaustion of the motive fluid through the inlet
port-hole I and the exhaust port-hole E is effected by means of the solid
cylindrical piston V, through which there is a single passage pl of the same
section as that of the inlet and exhaust port-holes, During the period of admission
.9
3

page_text: of the motive fluid, the valve piston is in its lowest position, being kept from
descending below its proper position in which the passage p, through the solid
valve piston is exactly opposite the inlet port-hole I, by the nut n¹ resting on the
lid n' screwed into the top of the valve cylinder through which the rod R rigidly
connected with the valve piston moves.
At the termination of the working stroke, the motive fluid at its maximum
pressure enters the valve chamber C* by the inlet port i, and by acting on the
underside of the valve piston forces it upwards until the passage plis opposite the
exhaust port-hole E, in which position it is kept by the continuance of the pressure
on the underside, until the pump barrel has been filled with fluid and the piston P¹,
has returned to the position shown in Fig 1, 2 and 3, and by pressing at its
upper end against the lid n³. In order to prevent loss of pressure in the valve
chamber at the instant the exhaust valve is opened and before the piston P¹ on
its return has covered the inlet port i, the inlet port i must be provided with a
reflux valve which will close, directly the pressure in the working cylinder drops
below that in the valve chamber C. When the pump barrel is filled, and the
piston P¹ is in the position shown in Figs 1, 2 and 3, a communication is formed
between the exhaust port e, and the passage p, shown in Figs 1 and 4, through
which the fluid in the valve chamber is at once discharged. The valve piston then
descends by its own weight into its lowest position and opens the inlet port-hole I.
In order that the valve piston V may move freely up and down the valve
cylinder C³, under all ranges of pressure in the inlet port I and working cylinder C³,
it is necessary that every pressure upon the valve piston V should be met by a
pressure or pressures equal in magnitude, but exactly opposite in direction. This
object has been effected in the following manner.
When the exhaust port is open, the pressure to be counterbalanced is the
pressure on the face of the solid valve piston V at the inlet port-hole I, and in
order to counterbalance this, two portholes B¹ are provided at the side of the
cylinder, opposite to that in which the inlet port-hole I is situated, their centres
being equidistant from the centre of the inlet port-hole, and their united areas
equal to the area of the inlet port-hole. The port-holes B₁ are kept constantly
filled with high pressure fluid, by means of the passages p³, which connect them
with the inlet supply pipe. When the inlet port is fully closed and the outlet port
fully opened, there must therefore be perfect equilibrium.
When the inlet port I is fully open and the outlet port E fully closed, there will
be three separate pressures to be balanced, viz: the pressure on the inside of the
exhaust port-hole E, and the pressures at the port-holes B', since these are always
kept in communication with the high pressure fluid in the supply pipe by means
of the passages p*. In order to counterbalance the pressure on the inside of the
exhaust port-hole E, two port-holes, B³, are provided on the opposite side of the
valve cylinder, their centres being equidistant from the centre of the exhaust
port-bole E, and their united areas equal to the area of the exhaust port-hole, and
to counterbalance the pressures exerted at the port-holes B¹ two portholes B³ are
provided exactly opposite to them in position and equal in area.
The port-
holes B2, B3, are kept in constant communication with the fluid in the working
cylinder C by means of the passages p³.
When the inlet, port I is fully open and the pressure in the working cylinder
practically equal to that in the inlet pipe, the opposing pressures exactly balance
each other. When moving from the position in which the inlet is open to that in
which the exhaust is open, after the closing of the inlet and previously to the
opening of the exhaust porthole, the pressure in the working cylinder will still be
equal to that in the inlet. supply pipe, and therefore the pressures on the opposite
sides of the valve piston at the inlet portholes equal to each other and also when
the valve piston is in the same position, when moving from the exhaust to the
inlet porthole, the pressure in the working cylinder will be equal to that in the
exhaust pipe and the pressures therefore on the piston valve at the exhaust port
the same on each side.

page_text: During the period of exhaust, the pressures at the ports B³ are practically
inappreciable. Further, in addition to balancing these opposite pressures, it is
necessary that the solid valve piston V should be so strong at its weakest point,
viz the passage p¹, as to be practically rigid under the action of the bending
moments of the opposite pressures. The fluid, which passes from the valve
chamber C, through the passages e, p, if a gas, escapes into the atmosphere, and
if a liquid, is discharged on to the top of the pump piston and flows into the
funnel shaped cistern M, through the orifice O, which also receives any liquid
which may leak between the sides of the pump and motive cylinder and their
respective pistons. The funnel shaped cistern is provided with a ball valve v,
which is kept closed by the pressure in the pump barrel during the working
stroke. At the commencement of the return stroke, the valve v opens instan-
taneously and allows the contents of the cistern M to descend into the pump
barrel C³ through the pipe N. In order to insure the effectual emptying of the
cistern M, before the inlet valve V₁ into the pump barrel opens, the valve seat
must be of such an area that the valve V₁ will not be lifted from its seat till the
Burface of the liquid in the cistern M descends below the level of the valve seat of
the valve v.
The weight of the pistons P¹ and P' must be counterbalanced by the weights W
suspended by ropes or chains passing over the pulley wheels wand attached to the
piston P in the manner shown in Fig. 2. The magnitude of the weights W must
be such as to cause the pistons, on the opening of the exhaust port E, to rise up to
the highest position necessary to connect the passage pt with the exhaust port e,
from the valve chamber.

page_text: I, WILLIAM DONALDSON, of 2 Westminster Chambers, Victoria Street, in the
County of Middlesex, Civil Engineer, do hereby declare the nature of this
invention, and in what manner the same is to be performed, to be particularly
described and ascertained in and by the following statement :-
===
This invention relates to pumping machinery allowing of the use of fluids of any
kind, either liquid or gaseous, under any given pressure (hereinafter called motive
fluid) for or towards pumping fluids of any kind either liquid or gaseous under the
same, or other pressure different from the pressure of the motive fluid.
The improvements are as follows, reference being made to the accompanying
drawing in which like letters describe like parts.
Fig. 1 is a sectional elevation through the centre of the pump barrel outlet
valve chamber V and inlet valve chambers V₁ and inlet valve V for admitting
liquid exhausted from the automatic valve chamber C3 and if necessary the liquid
exhausted from the high pressure cylinder c¹ and also leakage liquid into the
pump barrel c³ by the passage N. Fig. 2 is a sectional elevation taken at right
angles to the section Fig. 1 through pump barrel part of the motive cylinder c¹
and through portholes B¹ situated between the valve cylinder and motive cylinder;
Fig. 3 a sectional elevation likewise at right angles to section in Fig. 1 through
centre of the valve chamber C³. Fig. 4 a transverse section taken at P Q through
the inlet port I of the valve chamber. Fig. 5 a transverse section taken at G H
through the port B³. Fig. 6 a transverse section taken at K L through the
port B
The valve V which admits the motive fluid into the motive piston cylinder c
and allows it to escape at the completion of the stroke is loose, totally disconnected
from any other moving part of the machinery and is actuated solely by the
alternate admission of motive fluid, whilst under the maximum working pressure
at the end of the working stroke through an inlet porthole i provided with a
reflux valve leading from the motive cylinder into the valve chamber 03 and
lowered by the exhausting of the said fluid at the end of the return stroke through
an exhaust porthole e. When the high pressure fluid is a liquid the tension of the
air compressed in the valve chamber beneath the valve will raise the valve after
the inlet porthole I is closed. The rate of working of the pump varies auto-
matically with the quantity of fluid to be pumped in any assigned time.
The alternate admission and exhaustion of the motive fluid through the inlet
porthole I and the exhaust porthole, E is effected by means of the solid cylindrical
piston V through which there is a single passage p¹ of the same section as that of
the inlet and exhaust portholes.
During the period of admission of the motive fluid the valve piston V is in its
lowest position being kept from descending below its proper position in which the
passage p¹, through the solid valve piston is exactly opposite the inlet porthole I
by the nut n' resting on the lid n screwed into the top of the valve cylinder
through which the rod R rigidly connected with the valve piston moves.
At the termination of the working stroke the motive fluid at its maximum
pressure enters the valve chamber C³ by the inlet port and by acting on the
underside of the valve piston forces it upward until the passage p¹ is opposite the

page_text: exhaust porthole E in which position it is kept by the continuance of the pressure
on the underside due to the compression of air in the valve chamber C³ and by
pressing at its upper end against the lid, until the pump barrel has been filled
with fluid and the piston P¹ has returned to the position shown in Fig. 1 and 2.
In order to prevent the loss of pressure in the valve chamber at the instant the
exhaust valve is opened and before the piston P¹ on its return has covered the
inlet port i the inlet port i must be provided with a reflux valve which will close
directly the pressure in the working cylinder drops below that in the valve
chamber C³.
When the motive fluid is a liquid and the working pressure is low, it will not
produce enough tension in the air in the chamber C³ to cause the valve to rise to
its highest position. In this case the raising of the valve is completed by opening
a communication between the inlet porthole I and the valve chamber as soon as
the valve has closed the inlet port.
When the pump barrel is filled and the piston P¹ is in the position shown in
Fige 1 and 2 a communication is formed between the exhaust port e and the
passage p (shown in Fig. 1) through which the fluid in the valve chamber is at
once discharged.
The valve piston V then descends by its own weight into its lowest position and
opens the inlet porthole L.
In order that the valve piston V may move freely up and down the valve
cylinder C³ under all ranges of pressure in the inlet port I and working cylinder C¹
it is necessary that every pressure upon the valve piston V should be met by a
pressure or pressures equal in magnitude but exactly opposite in direction. This
object has been effected in the following manner.
When the exhaust port is open the pressure to be counterbalanced is the pressure
on the face of the solid valve piston V at the inlet porthole I and in order to
counterbalance this, two portholes B¹ are provided on the side of the cylinder
opposite to that in which the inlet porthole I is situated their centres being
equidistant from the centre of the inlet porthole and their united areas equal to
the area of the inlet porthole. The portholes B¹ are kept constantly filled with
high pressure fluid by means of the passages p' Fig. 4, which connect them with
the inlet supply pipe. When the inlet port is fully closed and the outlet port
fully opened there must therefore be perfect equilibrium. When the inlet I is
fully open and the outlet port E fully closed there will be three separate pressures
to be balanced viz the pressure on the inside of the exhaust porthole E and the
pressures at the portholes B' since these are always kept in communication with
the high pressure fluid in the supply pipe by means of the passages p³.
In order to counterbalance the pressure on the inside of the exhaust porthole E
two portholes B are provided on the opposite side of the valve cylinder, their
centres being equidistant from the centre of the exhaust porthole E and their
united areas equal to the area of the exhaust porthole and to counterbalance the
pressures exerted at the portholes B¹ two portholes B³ are provided exactly
opposite to them in position and equal in area.
The portholes B' B³ are kept in constant communication with the fluid in the
working cylinder 01 by means of the passages p*.
When the inlet port I is fully open and the pressure in the working cylinder
practically equal to that in the inlet pipe the opposing pressures exactly balance
each other.
When moving from the position in which the inlet is open to that in which the
exhaust is open after the closing of the inlet and previously to the opening of the
exhaust porthole the pressure in the working cylinder may have any value between
the highest and the lowest. The pressures on the opposite sides of the valve piston
at the inlet portholes and on the inside of the exhaust portholes will always be
balanced by the corresponding pressures in the portholes B' B* and B' respectively
and also when the valve piston is in the same position when moving from the
exhaust to the inlet porthole the pressure in the working cylinder will be equal to

page_text: that in the exhaust pipe, and the pressures therefore on the piston valve at the
exhaust port the same on each side. During the same interval and during the
period of exhaust the pressures at the ports B2 B3 are practically inappreciable.
Further in addition to balancing these opposite pressures it is necessary that
the solid valve piston V should be so strong at its weakest point viz the passage p¹
as to be practically rigid under the action of the bending moments of the opposite
pressures.
The passages connecting either the top or bottom valve chamber with the high
pressure fluid and exhaust ports can also be easily arranged so that the inlet port
should be situated above the outlet port conveying the fluid to and from the motive
cylinder.
The fluid which passes from the valve chambers C³ through the passages e, p' if
a gas, escapes into the atmosphere; and if a liquid is discharged on to the top of
the pump piston, and flows into the funnel shaped cistern M through the orifice O
which also receives any liquid which may leak between the sides of the pump and
the motive cylinder and their respective pistons. The funnel shaped cistern is
provided with a ball valve V which is kept closed by the pressure in the pump
barrel during the working stroke.
At the commencement of the return stroke the valve opens instantaneously and
allows the contents of the cistern M to descend into the pump barrel through the
pipe N. In order to insure the effectual emptying of the cistern M before the inlet
valve into the pump barrel opens, the valve seat must be of such an area that
the valve V¹ will not. be lifted from its seat till the surface of the liquid in the
cistern. M descends below the level of the valve seat of the valve V³.
Instead of using the arrangement shown in the drawings, the waste waters may
be pumped directly to their final destination by a pump worked automatically by
means of the alternations of pressure in the valve cylinder C³, so that the auxiliary
pump will make exactly the same number of strokes as the pump to which it is
attached.
Nearly all the waste water from the valve chamber may also be conveyed to the
same destination as the waste water from the power cylinder by a pipe or pipes
connected with the valve chamber and the residue a very small quantity can be
discharged into a small receiver which will have to be emptied from time to time.
The weight of the pistons P¹ and P' must be counterbalanced by the weights W
suspended by ropes or chains passing over the pulley wheels w and attached to the
piston P as shown in Fig. 2.
The magnitude of the weights W must be such as to cause the pistons on the
opening of the exhaust port E to rise up to the highest position necessary to
connect the passage p' with the exhaust port e from the valve chamber.
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
I claim is
In a pump actuated by fluid pressure the combination of the counterweighted
piston, the plunger forming its rod, and the slide valve with ports and passages
arranged for automatic action, substantially as herein described and illustrated by
the accompanying drawings.