Improvements in or relating to Bucket Pumps.
Year: 1894

page_text: Date of Application, 20th Sept., 1894
Complete Crocifination Loft 12th June 1805 Accented 17th Aug. 1895
Improvements in or relating to Bucket Pumps.
I, CONSTANTIJN PIETER HOLST, Gzoon, of 108, 2nd Jan Steen Street,
Amsterdam in the Kingdom of Holland, Engineer do hereby declare the nature of
this invention to be as follows:-
The object of this invention is to arrange piston pumps driven from cranks on
crank shafts in such a manner, that without the help of any air vessel a continuous
flow of the fluid passing the cylinders at a practically uniform speed is obtained.
For this purpose I employ several valve pistons either in one or in several
cylinders and I provide for means for driving the pistons from cranks. When the
valve pistons work in a single cylinder, they are driven separately by special rods,
which may be solid or hollow. The cranks are set at such angles, that the valve
pistons driven by them approach to and depart from each other alternately, so as
to canse the fluid to go successively through the various valve pistons. The
cylinder has about the same diameter as the suction and delivery pipe or it is a
little larger. There are no suction or delivery valves at all, so the fluid inside the
cylinder need not be stopped at the ends of the strokes as in common piston pumps.
When the several valve pistons work in separate cylinders, the latter are arranged
either in a line parallel to each other, or in pairs the one cylinder of which is
behind the other. The cylinders are further connected with each other by suitably
curved pipes of about the same diameter in such a manner, that the fluid goes in a
serpentine or sling like line through all the cylinders. When the cylinders are
arranged in a line and parallel to each other, the cranks driving the valve pistons
are set at such angles on one or several crank shafts, that the spaces between
the several valve pistons inside the cylinders and the connecting pipes are
increased and decreased alternately, so as to cause the fluid to flow continually
and to go successively through the various valve pistons. When the cylinders are
in pairs, the pistons of each pair sit on the same piston rod, while their cylinders
do not communicate with each other but with those of the other pairs.
1 further employ a suitable device for changing the constant revolving crank
motion into a nearly even reciprocating piston motion.
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The construction of this device depends upon the manner, in which the piston
rod is driven from the crank. When a crauk pin slot is employed, I divide the
rod between piston and crank pin slot, insert two levers and arrange two links
between the levers and the rod ends. The one lever hereinafter called "I"
connected through its link, called hereinafter "H" to the crank pin slot is provided
with a slot, in which the end of the other lever, hereinafter called "O," works.
The end of the lever "I" receives from the crank pin the well known so-called
pure harmonic motion," where the speed is greatest in the middle of the stroke
and is reduced to mil at the ends of the stroke. When the axle of the lever " 0"
is on the other side of the piston rod, its end describes a circle which intersects the
circle described by the end of the lever "1." In consequence of this the distance
of the end of the lever "O" in the slot from the fulcrum of the lever "I" varies,
so that the lever "0" receives a motion different from the pure harmonic motion
and of such a nature, that the speed is much reduced in the middle of the stroke
and increased near the ends of the stroke. When the axles of both levers "I" and
O" shorter than
O" are on the same side of the piston rod, I make the lever
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page_text: the lever "I," so that the lever "I" imparts to the lever "O" a motion similar to
the one described before.
When the motion of the crank pin is transmitted in the usual way by a
connecting rod to the piston rod, I arrange the device so as to give the lever "I" a
motion as similar as possible to the pure harmonic motion. Thereby the well
known faults of the connecting rod are obviated. The said slot of the lever " !
["
may then be either curved or replaced by a link, having the same length as the
radius of the curved slot and called hereinafter "M.' To carry this link "M"
the lever "I" is changed into a bellerank, at the free end of which the link "M"
is pivoted. The end of the link "M" is theu connected to the end of the piston
rod, while the link "H" at the bellcrank is pivoted at the cross head of the
connecting rod. Thus much the same motion is imparted to the piston by the
bellcrank, as before. When the axis of the piston rod and pump cylinder is turned
through an angle like that of the bellcrank, the latter becomes a simple lever.
The device may further be simplified in replacing the link "H" by the connecting
rod, which is linked direct to the lever "1."
The arrangement of the several valve pistons in one or several cylinders as
described above and the employment of the device for changing the constant
revolving crank motion into a nearly even reciprocating piston motion bave the
effect, that always one of the several valve pistons moves the whole fluid mass in
cylinders and piping during a certain portion of one crank revolution, whereupon
the other pistons take successively their turns. The fluid flows always forward
and at a nearly uniform velocity through the cylinder or cylinders and the piping.
Therefore the piston speed may be made much greater than is the case with the
common piston pumps, so that the pumps can be made comparatively smaller
in size.
When the pumps are driven direct by engines, the valve pistons being moved
with the steam pistons through suitable rods, the said device may be placed either
between the pump cylinder and the steam cylinder or between the latter and the
cross-head of the connecting rod.
Dated this 14th day of Santambor 1001
Improvements in or relating to Bucket Pumps.
I, CONSTANTIJN PIETER HOLST, Gzoon, of 108, 2nd Jan Steen Street,
Amsterdam in the Kingdom of Holland, 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 :-
The object of this invention is to arrange piston pumps driven from cranks on
crankshafts in such a manner, that without the help of any air vessel a continuous
flow of the fluid passing the cylinders at a practically uniform speed is obtained.
I will now proceed to describe my invention having reference to the figures on
the four sheets of drawings accompanying this my Complete Specification.
For the purpose explained above I employ several valve pistons either in one
or in several cylinders and I provide for means for driving the pistons from
cranks.
When the valve pistons A' A2 A3 work in a single cylinder B, Fig. I, they are
driven separately by special rods C1 C2 C3, which may be solid or hollow. In
Fig. 1 two of them, viz. C1 and C2, are solid, as they pass into the cylinder from
opposite sides. The third rod C³ is hollow, so as to let the second rod C2 go
through. In Fig. 2 four valve pistons A1 A2 A3 A4 are shown working within a
single cylinder, two of the rods C' C* being solid and the two other C³ Ct hollow.

page_text: The cranks are set at such angles, that the valve pistons driven by them approach
to and depart from each other alternately so as to cause the fluid to go successively
through the various valve pistons. When in Fig. 1 only one crankshaft is assumed,
say on the right hand, and all the rods are attached to this crankshaft by suitable
means, the cranks require to be set at about 120 degrees to each other. For
Fig. 2 in such a case the angles would have to be about 90 degrees. If there be
two crankshafts, i.e. one on each side of the cylinder B, of course, the two shafts
require to be so arranged, as to run synchronically, and the cranks are set parallel
to those of the one shaft, assumed to alone drive the various pistons.
The cylinder B has about the same diameter as the suction pipe R or the
delivery pipe S, or it is a little larger. There are no suction or delivery valves at
all, so the fluid inside the cylinder need not be stopped at the ends of the strokes
as in common piston pumps.
When the several valve pistons A work in separate cylinders B, the latter are
arranged either in a line (Fig. 4) parallel to each other, or in pairs (Fig. 3 and 5),
the one cylinder of which is behind the other. The cylinders are further
connected with each other by suitably curved pipes T U V W of about the same
diameter in such a manner, that the fluid goes in a serpentine line (Figs. 4 and 5)
or slinglike line (Fig. 3) through all the cylinders.
When the cylinders B are arranged in a line and parallel to each other (Fig. 4),
the cranks driving the valve pistons are set at such angles on one or several
crankshafts, that the spaces between the several valve pistons A inside the
cylinders and the connecting pipes are increased and decreased alternately, so as
to cause the fluid to flow continually and to go successively through the various
valve pistons. When the cylinders B are in pairs (Figs. 3 and 5), the pistous A
of each pair sit on the same piston rod C.
I further employ a suitable device for changing the constant revolving crank
motion into a nearly uniform reciprocating piston motion.
The construction of this device depends upon the manner, in which the piston
rod is driven from the crank.
When a crank pin slot P. Fig. 9, is employed, I divide the rod C between
piston A and crank pin slot P, insert two levers I O, and arrange two links H M
between the levers and the rod ends, i.e. the cross heads Q and N. The one
lever I, connected through its link H to the cross head Q and by means of the
rod E to the crank pin slot P, is provided with a slot, in which the end of the
other lever O works. The end of the lever I receives from the crank pin the well-
known so-called "pure harmonic motion," where the speed is greatest in the middle
of the stroke and is reduced to nil at the ends of the stroke. The axle of the
lever O being on the other side of the piston rod C, its end describes a circle,
which intersects the circle described by the end of the lever I. In consequence of
this the distance of the end of the lever O in the slot from the fulcrum of the
lever I varies, so that the lever O receives a motion different from the pure
harmonic motion and of such a nature, that the speed is reduced in the middle of
the stroke and increased near the ends of the stroke. To illustrate this, eight
different positions of the crank are shown in Fig. 9 by dotted lines set at 45 degrees
to each other and also the corresponding positions of the levers by such lines.
The stroke of the crank pin slot P being and the positions of the same for the
eight different crank positions being measured by the distances a bed, it will be
found, that a=d=1465 h and b =c=3535 h. To the distances a b c d for the
crank pin slot P and also the cross head Q correspond the distances a¹¹¹ d¹ for
the end of the lever O. Taking the levers I and O in the proportion shown
in Fig. 9 and the stroke of the end of the lever O as ', the distances are as
follows: a = d¹ = 2 h¹ and b₁ = c¹ = 3 h. On comparing the distances a b c d
with those a b c d¹ it will be obvious, that the motion of the lever O and thereby
also the motion of the piston is rendered more uniform than that of the crank pin
slot P and the cross head Q.
When the axes of both levers I and O are on the same side of the piston rod,

page_text: Fig. 10, I make the lever I shorter than the lever O, so that the lever I imparts
to the lever O a motion similar to the one described before.
Fig. 11 shows a variation of the preceding Fig. 10, the lever O being assumed
to be infinitely long, i.e. the piston rod C being guided by suitable bearings C¹ C².
When the motion of the crank pin is transmitted in the usual way by a
connecting rod E, Fig. 12, to the piston rod C, 1 arrange the device so as to give
the lever I a motion as similar as possible to the pure harmonic motion. Thereby
the well known faults of the connecting rod are obviated. The said slot of the
lever I (Fig. 11) may then be either curved or replaced by the link M (Fig. 12),
having the same length as the radius of the curved slot. To carry this link M
the lever I is changed into the bellerank IK L, at the free end M' of which the
link M is pivoted. The end of the link M is then connected to the end of the
piston rod C, i.e. to the cross head N connected thereto, while the link H at the bell-
crank I KL is pivoted at the cross head O of the connecting rod E. Thus much
the same motion is imparted to the piston A by the device, viz. the bellcrank I KL
and the links H and M, as before.
When the axis of the piston rod C and pump cylinder is turned through an
angle like that of the bellcrank I K L, Fig. 13, the latter becomes a simple lever I,
while the links H M and the cross heads QN remain the same as before.
This device may further be simplified in changing the link H into a connecting
rod, see Fig. 14, which is linked direct to the lever 1.
Hitherto the variations of the device have been shown and explained by skeleton
drawings (Fig. 9 to 14) to facilitate the study of the same. It is, however, very
For
easy to carry out any of these variations into effect in a practical manner.
example the device shown in Fig. 12 may be constructed in the manner illustrated
by Figs. 15 and 16, where similar letters of reference indicate similar parts. The
bellerank KL is made in two halves, which are united by a stay in the
prolongations 12, the pin M' and the axle 1', so as to render the whole strong and
reliable. There are two links H, which are placed at the sides of the bellcrank,
so as to allow of the latter passing between them. The link M is single and is
connected with the piston rod C by means of the cross head N. Where it is so
preferred, the bellerank I KL may be replaced by two single levers I outside and
two single levers K within the ground plate X. In this case the cross head Q,
of course, requires to be extended beyond the guides Q Q and the links H H
will have to be placed on the outside of the guides N¹ Q'N' Q¹.
The arrangement of the several valve pistons in one or several cylinders as
described above and the employment of the device for changing the constant
revolving crank motion into a nearly uniform reciprocating piston motion have the
effect, that always one of the several valve pistons moves the whole fluid mass in
cylinders and piping during a certain portion of one crank revolution, whereupon
the other pistons take their turns successively. The fluid flows always forward
and at a nearly uniform velocity through the cylinder or cylinders and the piping.
Therefore the piston speed may be made much greater, than is the case with the
common piston pumps, so that the pumps can be made comparatively smaller
in size.
Fig. 6 shows an example of how a pump B placed at a right angle to the axis of
a steam cylinder F may be driven from the back lengthening G of the steam
piston rod.
When the pumps are driven direct by steam engines, the valve pistons being
moved with the steam pistons through suitable rods, the said device may be placed
either between the pump cylinder B and the steam cylinder F, Fig. 8, or between
the latter and the crosshead of the connecting rod, Fig. 7.
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 :-
1. A pumping arrangement for furnishing the fluid in a continuous stream at a

page_text: nearly uniform velocity consisting in one or several pump cylinders B inserted in
a single piping, several valve pistons A working in said pump cylinder or pump
cylinders B and being driven separately or in pairs from cranks set at such angles,
that the spaces between the several valve pistons A are increased and decreased
alternately and successively, and a device inserted in every piston rod C for
equalizing the reciprocating motion, substantially as set forth.
2. In a device named in the first claiming clause for equalizing the reciprocating
motion of a piston rod driven from a crank, the combination with a crank pin
slot P, a slotted lever I, a link H connecting the lever I with the crank pin slot P
either direct or by suitable means, and a lever O guided at the end by the slot of
the lever I, of a link M connecting the lever O with the piston rod C either direct
or by suitable means, the named parts being either single or double, as the case
may be, substantially as set forth.
3. In a device named in the first claiming clause for equalizing the recipro-
cating motion of a guided piston rod driven from a crank, the combination with a
crank pin slot, a slotted link I, and a link H connecting the lever I with the crank
pin slot either direct or by suitable means, of a block attached to the piston rod C
and adapted to slide in the slot of the lever I, the named parts being either single or
double, as the case may be, substantially as set forth.
4. In a device named in the first claiming clause for equalizing the reciprocating
motion of a piston rod driven from a crank, the combination with a crank, a bell-
crank IKL or its equivalent, and a link H connecting one end of the bellcrank
or its equivalent either with the crosshead Q of the connecting rod or direct with
the crank pin, of a link M connecting the other end of the bellcrank or its
equivalent with the crosshead N of the piston rod, the named parts being either
single or double, as the case may be, substantially as set forth.
Dated this 8th day of June 1895.
CONSTANTIJN PIETER HOLST, Gzoon.