Year: 1897

page_text: Date of Application, 7th Dec., 1897-Accepted, 8th Jan., 1898
I, WILLIAM HUMPHREY WHEATLEY, of the Firm of Wheatley and Mackenzie,
Engineers and Patent Agents, of 40 Chancery Lane, London, W.C., do hereby
declare the nature of this invention and in what manner the same is to be per-
formed, to be particularly described and ascertained in and by the following
statement:
-
This invention relates to power pumps of the class in which two single-acting
plungers, operating in conjunction with a single discharge passage, are reciprocated
by separate crank connections, at an equal number of strokes per minute, but with
a slow working stroke and quick return stroke, so that the water column is never
for an instant relieved of the actuating impulse of one of the plungers, and is
thereby maintained in continuous flow. The object of the invention is to provide
an improved power head for actuating the plungers in the manner described, and
it consists in the matters hereinafter described and claimed.
In a machine embodying my invention the driving mechanism for each plunger
embraces a crank shaft or equivalent rotative part, having a crank pin to which
the plunger connecting rod is attached, and a separate rotative driving part
arranged eccentrically to the first part, upon an axis parallel to the axis of
said first part. One of said parts is provided with a wrist pin and the other with
a groove into which the wrist pin projects and within which it slides as it approaches
to and recedes from the centre of revolution of the grooved part in its eccentric
movement about the same. In many instances the driving part will be a second
shaft arranged almost end to end with the crank shaft, but offset somewhat there-
from, so that the axes of the two shafts are parallel instead of continuous. At their
adjacent ends the two shafts will be provided with crank arms or the like, which
rotate in parallel planes in close proximity to each other, one of said crank arms
being provided with the wrist pin and the other with the co-acting groove, as
described. The driving part is given a uniform rotary movement from any
suitable source of power, and transmits a rotary movement to the driven or pump
crank part, through the engagement of the wrist pin and slot or groove. Owing to
the eccentricity of the parts, however, the rotary movement resulting in the driven
part is not uniform, but is alternately faster and slower in each revolution and
the relative arrangement of the several elements is made such that the operative
or discharge stroke of the connected plunger occurs during the slow part of the
revolution of its crank while its return or idle stroke occurs during the other or
rapid part of the revolution. The driving connections are precisely similar for
hoth plungers of the pump and the number of revolutions per minute is the same
in each, the driving parts being ordinarily provided with intermeshing gears of
equal diameter. The two mechanisms are, furthermore, so arranged with respect

page_text: to each other that the strokes of the plungers occur in alternation, i.e., the return
stroke of one plunger takes place during the discharge stroke of the other plunger.
Inasmuch, however, as each discharge stroke occupies a considerably longer interval
than the return stroke, for the reasons herein before stated, each plunger completes
its return and commences its discharge stroke again before the discharge stroke of
the other plunger is completed. The column of water in the common discharge
pipe, therefore, is never free from the actuating impulse of at least one of the
plungers, and with a proper proportion and correct relative arrangement of the
parts the discharge is not only continuous, but, in a large degree, approximates
a constant flow.
A further development of the invention has for its object to reduce the accelera-
tion and consequent shock ordinarily incident to the beginning and early part of
each working stroke of a crank driven plunger, without reducing the capacity of
the pump or the number of strokes per minute, by securing a slower movement
of the crank as it passes its lower dead center and prolonging the period over which
the increase of plunger speed to its maximum is distributed, and by subsequently
making up for the reduced amount of work performed during this period, by
prolonging the period of maximum discharge to a later point in the revolution
and concluding the stroke more abruptly as the crank approaches its upper dead
center. To accomplish this result the pump crank is so located with reference
to the groove that the wrist pin enters upon that portion of its orbit during which
it effects the slower half revolution of the crank shaft somewhat in advance of the
moment at which the pump crank enters upon its upward or working movement,
while the groove itself is arranged at such an angle that the sliding of the wrist
pin within the groove produces in effect a rocking motion of the crank shaft by
which the pump crank falls still further behind in the first portion of its upward
movement, but begins to overtake the wrist pin again in the latter portion of its
movement, and finally completes said movement at a rate of speed due to the
previous entrance of the wrist pin upon that portion of its orbit during which it
effects the faster half revolution of the crank shaft.
An actuating mechanism constructed in accordance with my improvements is
particularly well adapted for use in that class of lift pumps in which two valved
plungers are arranged one above the other in the same cylinder. Pumps of this
kind are commonly employed in bored wells of small diameter, and the cylinder
proper usually constitutes one sect on of a straight continuous pipe which also
forms the suction and discharge pipes, and may serve as the casing of the well.
When the well is of considerable depth, as is frequently the case in practice, the
weight of the water within said pipe is very great, and the shock incident to any
sudden checking of acceleration of its flow is correspondingly severe. The more
uniform movement of the column resulting from the improvements described
relieves the pump to a material extent from such shocks, and greatly reduces the wear
and tear. It also increases the efficiency of the apparatus by decreasing the
loss of power due to the dissipation of the momentum of the column incident to
an intermittent movement.
The invention will be more fully understood from the following detailed descrip-
tion of the construction illustrated in the accompanying drawings, which show
some of the forms in which the improvements may be practically embodied.
In said drawings:-
Figure 1 is a vertical sectional elevation of a deep well pumping plant of the
character herein before referred to.
Figure 2 is a top plan view of the actuating mechanism thereof.
Figure 3 is a transverse sectional view taken on line 3-3 of Figure 2.
Figure 4 is an enlarged end view of the pump crank shaft showing the grooved
crank.
Figure 5 is a side view thereof.
Figure 6 is a detailed end view of a grooved crank showing the slide and wrist
Din within it.

page_text: Figure 7 is a diagrammatic view showing the relative position of the parts of
the pump shown in Figures 1 and 2 at various points in the revolution.
Figure 8 is a similar view showing the relations of such parts as they would be
if the grooves were in the same radial planes with the pump cranks.
Figure 9 is a graphical lay-out of the discharge and suction lines produced by
mechanisms operating as shown in Figures 7 and 8.
Figure 10 is a similar view of the discharge and suction lines of the ordinary
double plunger lift pump.
Figure 11 is a diagrammatic view showing the relative relations of the crank
and wrist pins to the grooves, when the driving shafts are arranged in a common
plane with the two crank shafts and between the latter.
Figure 12 is a similar view, showing the relations of said parts in a construction
in which the driving shafts are arranged above the crank shafts.
Figure 13 shows a double plunger lift pump with separate cylinders; and
Figure 14 a more compact arrangement of the driving parts.
In said drawings A designates the pump cylinder, and B B are valved plungers
arranged one above the other within the cylinder. Said plungers may be of any
preferred construction having valves such as 6 61, which open freely to permit the
free upward movement of the current, but close instantly to prevent any return or
downward movement thereof. The cylinder A is in effect simply a lower section
of a continuous vertical pipe A', but is preferably made of slightly reduced diameter
in order to permit the plungers B B to be readily withdrawn for inspection and
repair. The pipe A¹ depends from a connected cast iron chamber A2 which rests
From
upon a suitable foundation beneath the operating mechanism of the pump.
the chamber A2 a pipe A³ leads to any connection or point of discharge desired,
as, for example, to the service pipes or reservoir of a water works system.
The operative mechanism of the pump is herein shown as suported by 1-beams C
above a pit C¹, at the bottom of which the chamber A2 is located. Parallel crank
shafts D D are journalled upon a base plate C that rests on the I-beams C, and
are provided with cranks d and d¹, from which connecting rods E E¹ extend down-
wardly to cross-heads F F¹. The latter are arranged to reciprocate vertically
between guides f f¹ that are rigidly supported within the pit in any suitable
manner, the connecting rod E being made of greater length than the connecting
rod E and the cross-head F being located at a correspondingly lower level than
the cross-head F. Said cross-head F is rigidly attached to the upper end of a
tubular plunger rod 62 which extends vertically downward through a stuffing
box a in the chamber A2 and carries the upper plunger B at its lower end. The
cro-head F is rigidly attached to a smaller plunger rod 63 which passes down
through the hollow plunger rod 62, and supports the lower plunger B¹. The plunger
rod is free to reciprocate within the plunger rod b and a stuffing box b' is pro-
vided at the cross-head F, or at any other suitable point, to prevent leakage
through the hollow rod 62 around said inner rod 6³.
The crank shafts D) D₁ are rotated by driving shafts G G which are journalled
the same horizontal plane with the crank shafts, but are offset laterally there-
from, each driving shaft being here:n shown as located on the side of its crank
shaft toward the other crank shaft, and the eccentricity of the driving shaft to
its crank shaft being the same in each case. Said driving shafts are designed to
rotate at the same rate of speed and are in this instance provided with intermeshing
gears G2 G3 of equal diameter. The driving power is applied in any suitable
manner, as, for example, by a large gear G4 which is keyed to the end of the shaft
G and intermeshes with a driving pinion Go on a counter shaft Go, and the direc-
tion of rotation is such that the shaft and gears move upwardly from their inner
or adjacent sides. The ends of the driving shafts nearest the crank shafts carry
crank arms g g from the faces of which wrist pins g² g³ project in the direction
of the crank
the
shafts, and
latter
their
are provided at
12 173 which are grooved on
ends with crank
arms
adjacent
their outer
faces at d to receive the wrist pins 02 93. To reduce the friction and wear

page_text: the wrist pins, as herein shown, do not come directly into contact with the walls
of the grooves d, but are journailed within the slides g g³ which fit and are
adapted to reciprocate within said grooves, but the resulting movement is obviously
the same as though such slides were omitted. Each wrist pin travels in an
eccentric circle about the adjacent crank shaft and exerts a continuous pressure
in one rotative direction upon the grooved crank thereof, the angular velocity
of the rotary movement thus produced in each crank, however, varies throughout
each revolution and at any given instant will be faster or slower than the angular
velocity of the driving shaft in the proportion that the distance from the wrist
pin to the axis of the driving shaft at the instant is greater or less than its distance
from the axis of the crank shaft. The relative angular location of the pump
crank and grooved crank on each shaft is nearly the same and the upward and
downward movement of the pump crank consequently occurs in substantial coin-
cidence with the corresponding movements of the wrist pins. During its down-
ward movement the latter is nearer the crank shaft and in accordance with the
rule above stated, imparts an increased angular velocity to the latter, and a conse-
quent rapid downward movement of the pump crank. During its upward move-
ment the wrist pin is farther from the crank shaft and imparts to it a decreased
angular velocity, thereby causing a slow upward movement of the pump crank.
The lifting or working stroke of each plunger is therefore correspondingly slower
than its downward stroke and as the intermeshing gears G2 and G³ on the driving
shafts are adjusted to maintain the two pump cranks in relatively opposite portions
of their respective paths of revolution, the quick downward stroke of one plunger
occurs during the long upward stroke of the other plunger and the upward strokes
of both plungers consequently overlap at both ends. The working stroke of each
plunger, furthermore, occurs at the time that its operating wrist pin is engaging
the outer end of the grooves d', and is consequently working with its longest
leverage, and with the least necessary strain on the driving parts.
While the relative angular location of the grooved cranks and pump cranks on
the shafts is nearly the same, as herein before stated, the grooves d do not, in the
approved construction shown, stand exactly in the radial planes of the pump cranks,
but for the purpose of still further improving the effective action on the water
column are non-radial, being herein shown as arranged to intersect the said planes
at the limit of innermost movement of the wrist pins, and extend outwardly and
forward from such points of intersection at a considerable angle, in this instance
thirty degrees, with said planes, i.e., the grooves are so located with reference
to the pump cranks that when either wrist pin reaches its outermost position and
stands in the same horizontal plane with its driving and crank shafts, the pump
crank pin will also stand in that plane, and the grooves d will extend outwardly
from the wrist pin in front of the pump crank and at the above mentioned angle
therewith (see Figure 11). With this construction the pump cranks lag behind
the wrist pins in the lower half of each revolution and overtake them again in the
upper half revolution. The crank shafts are consequently rotating at a less angular
velocity, when the pump cranks begin their upward or working movement, than
would otherwise be the case, and the initial upward movement of the plungers is
correspondingly slower. The lag of the crank, moreover, continues to increase
almost to the middle of the upward movement, and reduces the acceleration
naturally incident to the first quarter of a crank motion, thereby correspondingly
reducing the extra load thrown on the plunger at each revolution by reason of such
acceleration. On the other hand, the return forward movement of the pump crank
relatively to the wrist pin which begins at the middle of the upward stroke, acts
in opposition to the decrease in plunger speed incident to the second quarter or a
crank motion, and prolongs the effectiveness of the stroke to a later point in the
revolution. In other words, the effect of the above described peculiar relative
location of the pump cranks and grooves, is to more equally distribute the work
throughout the entire stroke and reduce the wear and tear accordingly. With
the ordinary crank movement the extra load thrown on the plunger in the first

page_text: half of each working stroke by reason of the acceleration imparted to the column
of water during this period constitutes a very material portion of the total maxi-
mum load which the working parts must be designed to carry, and the suddenness
with which the load is applied produces a shock which adds very greatly to the
tendency toward breaking. Any reduction in the load due to acceleration, there-
fore, results directly in decreasing the required strength of the parts, and reducing
the frequency of break downs. A somewhat similar modification of the acceleration
effects would be accomplished by making the grooves d radial and arranging the
pump cranks at a suitable angle behind them, but the particular construction
shown is deemed to be the most effective yet devised for the purpose. It will,
oreover, be understood that in any case the relative angular arrangement of the
grooved cranks and pump cranks is directly dependent upon the relative location
of the driving and crank shafts, so that if the driving shafts were placed in any
other position with relation to their crank shafts than that shown, viz. on the
inner sides of and in the same horizontal plane with said crank shafts, a corre-
sponding change would have to be made in the position of the pump cranks with
relation to the grooved cranks, since otherwise the upward or working movement
of the pump cranks would not occur during the period of minimum angular velocity
of the crank shafts. For example, in Figure 12 I have indicated a construction
in which the driving shafts are arranged directly above the crank shafts instead
a level therewith, and in which the pump cranks are accord-
ingly located about 90 degrees behind the position before described;
and an indefinite number of other similar changes of arrangement
might easily be suggested. In both Figures 11 and 12 c c designates the crank
shaft centers, do the driving shaft centers, cp the crank pins, and w p the wrist
pins.
of on
The relative positions of the two plungers, and of the cranks and wrist pins at
various parts of the stroke are diagrammatically shown in Figure 7. In said
Figure H H designates the centers of the crank shafts and I I¹ the centers of the
driving shafts. The larger circles h h¹ struck from the centers H H indicate the
paths of the pump crank pius, while the smaller circles struck from the centers
1 I indicate the paths of movement of the wrist pins. The vertical lines J J¹
indicate approximately the movement of the cross-heads and consequently
of the plungers, and the lines J2 J3 show the relative positions of
the connecting rods at the time the right hand plunger reaches the
upper limit of its stroke, no account being made in this diagram
of the difference in length of the connecting rods. The points numbered 1
on each of the circles are those occupied by the wrist pins at the time the
right hand plunger is at the uppermost point of its stroke, the left hand plunger
at this point being on the upward move in a position about one-sixth of the entire
length of its stroke from the bottom thereof. The succeeding correspondingly
numbered points, 2, 3, 4, etc., designate equal divisions of the circles i¹,
which divisions represent the distances travelled by the wrist pins
in equal periods of time throughout the entire revolution. The lines
drawn through the numbered points and which project outwardly and forwardly
therefrom in the direction of rotation of the shafts as indicated by the arrows,
represent the center lines of the grooves which receive the wrist pins, and the points
numbered 1º, 2º, 3º, etc., on the larger circles h h¹ indicate the points occupied by
the crank pins at the time the wrist pins occupy the points 1, 2, 3, etc., respec-
tively. It will be observed that the distances between the points 1º, 2º, 3º, etc.,
en the outer portions of the larger circles h h¹ are much greater than the distances
between the points 1, 2, 3, etc., on the smaller circles and are still greater than
the distances between the similar points on the inner portions of the larger circles,
and, since these distances represent the travel of the crank and wrist pins during
equal intervals of time in different portions of their revolution, it is evident that
the cranks move more and more rapidly as they approach their outermost hori-
zontal positions and less and less rapidly as they approach their innermost horizontal

page_text: positions as herein before more particularly set forth. The points numbered 1,2,3,
tc., on the vertical lines J J, designate the various positions occupied by the
plungers at the time their crank pins are in the positions designated 1, 2, 3, etc.,
respectively, and the points numbered the same on the two lines designate the
positions of the two plungers at the same moment in various parts of their stroke.
The numbers along the inner sides of the lines J J' mark the progressive movements
of the plungers on their upward strokes and will be observed to be spaced closer
together than the numbers on the outer sides of the lines which mark the progres-
sive downward movements of the plungers, and the more rapid descent of the plungers
is thus indicated. It will also be observed that the inner numbers are spaced
closer together at the lower ends of the lines, thus indicating the relatively slow
beginning and rapid termination of each upward stroke. By a comparison of the
two sides of the diagram and of the correspondingly numbered points thereon, the
relative positions of the several parts at any given moment may readily be
determined.
In Figure 8 I have shown a similar diagram which differs from that shown in
Figure 7 only in representing the center lines of the grooves as located in the same
radial planes with the pump crank pins. The principal practical difference between
such a construction and that previously described lies in its failure to accomplish
the desired reduction in the initial acceleration of the column with the advantages
incident thereto.
In Figure 9 I have shown a graphical representation in which the curved
lines K and K' represent the velocity lines of the two plungers in the construction
shown in Figures 1 and 2. Horizontal distances in this diagram represent piston
movement and vertical distances velocity. Those portions of these lines above the
horizontal line L, or the line of no velocity, correspond with the upward or working
movement of the stroke, while those portions below the line L correspond with the
downward or return stroke, the direction of movement being understood to be from
right to left as indicated by the arrows. It will be observed that the portions of
the lines K K above the base line overlap considerably, thus indicating the over-
lapping of the working strokes of the two plungers, as herein before described,
and their long flat curves show the prolonged slow action of the working stroke
when compared with the short rapid action of the return stroke as indicated by the
sharp curves below the base line. The lines M and M' on the same Figure are
such as would be produced under the same circumstances by a mechanism of the
kind shown in Figure 8, or one in which the grooves are arranged in the same
planes with the pump cranks. The flatter curves of the lines K K¹ at the beginning
of the upward stroke as well as the fuller curvature of said fines toward the termi-
nation of the stroke indicates the more gradual acceleration and better distribution
of the work due to the peculiar angular relations of the grooves and crank shafts.
The points of intersection k of the lines K K₁ and the corresponding points of
intersection of the lines M M¹ indicate the points at which the load of the ascending
column is transferred from one to the other and mark the minimum discharge,
and it will be observed that the distance of these points above the base line L is
nearly three-fourths of the distance from said line to the highest point of the
curves, thus indicating a minimum discharge equal to nearly three-fourths of the
maximum discharge. In an ordinary double plunger lift pump, on the other hand,
the velocity lines of the two plungers and of the discharge may be represented
by a succession of curves N N¹, as shown in Figure 10, which intersect on the base
line or line of no velocity, and indicate a total cessation of flow at two points in
each revolution.
In the construction illustrated in Figure 13 my improvements are shown as
applied to a lift pump having two valved plungers () ()₁ arranged in separate
cylinders P P which connect with a common discharge pipe P. Lift valves pp
are in this case provided at the lower ends of the cylinders and the suction
pipes P3 P3 may be separate or communicating. The flow in the discharge pipe in
this construction will be substantially the same as in the construction first shown.

page_text: Figure 14 is a plan view similar to Figure 2 but showing a more compact design
of driving mechanism. In this construction the intermeshing gears G2 G3 rotate
on stud shafts g6 in close proximity to the grooved cranks d² d³, and the wrist
pins g g project from the faces of said gears into the grooves d⭑.
While the improvements set forth are particularly applicable to doable plunger
pumps and especially to lift pumps of the type more particularly illustrated, it will
be understood that in some of its features the invention will also be advantageous
as applied to single plunger lift pumps, especially in so far as it achieves a reduction
in the acceleration and a better distribution of the load throughout the working
stroke. It will also be understood that while wrist pins and grooves have been
found to be the most desirable means yet known of communicating motion between
the eccentrically abutting driving and crank shafts, yet, nevertheless, any other
form of connection resulting approximately in the movement set forth may be
used and is comprehended within the broad spirit of my invention, and various
changes in the details of construction are obviously permissible.
Having now particularly described and ascertained the nature of my said in-
vention, and in what manner the same is to be performed, I declare that what I
claim is:-
1. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, separate rotative driving parts, each
arranged eccentric to the crank element driven thereby, and rotating sliding means
applying the driving power between each driving part and its crank element in a
circular orbit concentric with the axis of the one and eccentric to the axis of the
other.
2. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, separate rotative driving parts each
arranged eccentric to the crank element driven thereby, and driving connections
between each driving part and its crank element consisting of a wrist pin on the
one and a groove in the other into which the wrist pin projects.
3. An actuating mechanism for double plunger pumps, comprising rotative crank
elements connected with the plungers, separate rotative driving parts, each arranged
eccentric to the crank element driven thereby, and provided with intermeshing
gears of equal diameter, and driving connections between each driving part and its
crank element whereby the latter moves alternately slower and faster in each
revolution, the parts being adjusted to effect the idle or return movement of one
plunger during the working stroke of the other plunger.
4. A pump provided with two single acting plungers, rotative crank elements
connected with the plungers, separate rotative driving parts, each arranged eccen-
tric to the crank element driven thereby, gearing for rotating said driving parts
at equal speeds, and driving connections between each driving part and its crank
element consisting of a wrist pin on the one and a groove in the other into which
the wrist pin projects.
5. A pump provided with two single acting plungers, rotative crank elements
connected with the plungers, separate driving shafts each arranged eccentric to the
crank element driven thereby and provided with intermeshing gears of equal
diameter, and driving connections between each driving shaft and its crank element
consisting of a wrist pin on the one and a groove in the other into which the wrist
pin projects.
6. An actuating mechanism for double plunger pumps, comprising rotative
crank shafts connected with the plungers, rotative driving parts each arranged
eccentric to the crank shaft driven thereby, a grooved crank on each crank shaft
adjacent to its driving part and wrist pins on the driving parts engaging the
grooves, substantially as described.
7. An actuating mechanism for double plunger pumps, comprising rotative crank
shafts connected with the plungers, inter-geared rotative driving shafts each arranged
eccentric to the crank shaft driven thereby, grooved cranks on the crank shafts

page_text: and a wrist pin on each driving shaft engaging the grooved crank of the crank
shaft driven thereby.
8. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, separate rotative driving parts each
arranged eccentric to the crank element driven thereby and upon an axis located
in the same plane with and between the axes of the crank elements, and driving
connections between each driving part and its crank element consisting of a wrist
pin on the one and a groove in the other engaged by said pin.
9. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, separate rotative driving parts each
arranged eccentric to the crank element driven thereby, and driving connections
between each driving part and its crank element consisting of a wrist pin on the
one and a groove in the other into which the wrist pin projects, the relative angular
arrangement of the parts being such as to retard the initial working movement
of the plunger.
10. The combination with a pump plunger of a crank element connected there-
with, a rotative driving part arranged eccentrically to said crank element, and
driving connections between the crank element and driving parts, con-
sisting of a groove in the one and a wrist pin on the other en-
gaging said groove, said groove being arranged angularly in advance of the crank
pin and on a line intersecting the radial plane of the crank between the crank pin
and its center of rotation, substantially as described.
:
11. The combination with a pump plunger, of a crank element connected there-
with, a rotative driving part arranged eccentrically to the crank element and
driving connections between the crank element and driving part, con-
sisting of a groove in the one and a wrist pin on the other which
engages said groove, said groove being arranged angularly in advance of the crank
pin on a line intersecting the radial plane of the crank approximately at the
point occupied by the wrist pin at the innermost end of its travel within the groove,
ubstantially as described.
12. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, rotative driving parts each arranged
eccentric to the crank e'ement driven thereby, and driving connections between
each driving part and its crank element consisting of a wrist pin on the one and a
groove in the other engaged by said wrist pin, each groove being arranged angularly
in advance of the connected crank element, substantially as described.
13. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, rotative driving parts arranged eccen-
trically to the crank elements and driving connections between the crank
elements and driving parts, consisting of wrist pins on the one and
grooves in the other into which the wrist pins project, said grooves being
arranged angularly in advance of the crank pins on lines which intersect the radial
planes of the cranks between the crank pins and their center of rotation.
14. The combination with two valved plungers arranged within a single cylinder,
of rotative crank elements connected with the plungers, separate rotative driving
parts, each arranged eccentric to the crank element driven thereby, and rotating
sliding means applying the driving power between each driving part and its crank
clement in a circular orbit concentric with the axis of the one and eccentric to the
axis of the other.
15. The combination with two valve plungers arranged within a single cylinder,
of rotative crank elements connerted with the plungers, separate rotative driving
parts each arranged concentric to the crank element driven thereby, and driving
connections between each driving part and its erank element consisting of a wrist
pin on the one and a groove in the other into which the wrist pin projects.
16. The combination with two valve plungers arranged within a single cylinder,
of rotative crank elements connected with the plungers, separate rotative driving
parts, each arranged eccentric to the crank element driven thereby and provided

page_text: with intermeshing gears of equal diameter, and driving connections between each
driving part and its crank element whereby the latter moves alternately slower
and faster in each revolution, the adjustment being such as to effect the idle or
return movement of one plunger during the working stroke of the other plunger.
17. The combination with two valve plungers arranged within a single cylinder,
of rotative crank shafts connected with said plungers, secondary grooved cranks on
said crank shafts, separate rotative driving parts each arranged eccentric to one of
the crank shafts, and a wrist pin on each driving part engaging the grooved crank
of the adjacent shaft.
18. The combination with two valve plungers arranged within a single cylinder,
of rotative crank shafts connected with said plungers, separate inter-geared driving
parts each arranged eccentric to the crank shaft driven thereby, and a co-acting
groove and wrist pin operatively connecting each driving part and crank shaft.
19. The combination with two valve plungers arranged within a single cylinder,
of crank shafts connected with said plungers, secondary grooved cranks on said
crank shafts, separate driving parts each arranged eccentric to the crank shafts
upon axes located between and in the same plane with the crank shafts, and a
wrist pin on each driving part engaging the adjacent grooved crank.
20. The combination with two valve plungers arranged within a single cylinder,
of rotative crank elements connected with the plungers, separate driving parts, each
arranged eccentric to the crank element driven thereby, and driving connections
Letween each crank element and its driving part, comprising a wrist pin on the
cne and a groove in the other into which the wrist pin projects, the groove being
arranged angularly in advance of the connected crank element.
21. The combination with two valved plungers arranged within a single cylinder,
cf rotative crank elements connected with said plungers, rotative driving elements
arranged eccentrically to said crank elements, driving connections between the
crank elements and driving parts comprising wrist pins on the one engaging grooves
in the other, said grooves being arranged angularly in advance of the crank pins
upon lines intersecting the radial planes of the crank between the crank pins and
their center of rotation.
22. An actuating mechanism for double plunger pumps, comprising rotative
crank elements connected with the plungers, separate rotative driving parts, each
arranged eccentric to the crank element driven thereby, and driving connections
between each driving part and its crank element, consisting of a wrist pin on the
one and a non-radial groove in the other into which the wrist pin projects.
Dated this 7th day of December 1897.
WHEATLEY & MACKENZIE,
40 Chancery Lane, London, W.C., Agents.