Pump and Windmill Connection Page: 3 of 4
[1], 3 p. : ill. ; 23 cm.View a full description of this patent.
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1,067,848
pin 26, in engagement with one of the aper-
tures 27 through said lever 10. Similar
apertures 27 are provided near the pivotal
points 11, 19, 21 and 23, so that the leverage
15 of the levers 10, 17 and 22 may be regulated
according to the attending circumstances.
In order that the objects and operation of
my improved transmission mechanism may
be better understood, it may be stated that
10 the driver rod 7, when actuated by a wind
mill of ordinary construction, moves with a
uniformly accelerated and retarded stroke,
on account of the usual crank (not shown),
with which the driver rod connects; the
15 greatest speed of said driver rod occurring
at the middle of its stroke, the speed being
reduced to the minimum as it approaches
the ends of its stroke. Moreover, more
power is required for moving the driver rod
20 through the middle of its stroke than at the
ends thereof, as is well known to persons
familiar with the art. The arrangement of
links and levers constituting my invention
partially counteracts the foregoing variable-
25 ness of the stroke as follows: Assuming that
the driver rod 7 is in its lowermost position
when the pivots 18, 19 and 21 were in aline-
ment and that said rod 7 is now making its
upward stroke, in Fig. 1, while the left-hand
30 end of the lever 10 is being drawn upward,
and its right-hand end is moving downward
and drawing the lever 17 downward, by
means of the link 14, and drawing the right-
hand end of the lever 22 downward by
35 means of the link 20 and lever 17. It is
obvious that this operation causes the left-
hand end of the lever 22 to move upward
and carry the plunger rod 6 therewith. It
will be seen that the lever 17, while moving
40 downward, also moves rightward, as indi-
cated by the arcuate broken lines through
the pivots 16 and 19. Because of the excess
of leverage in favor of the wind mill con-
necting or driving rod 7 and link 8, it will
45 be seen that the pivot 9 travels approxi-
mately twice the distance of the pivot 24,
or in other words, the link 8 and rod 7
travel approximately twice as fast as the
plunger rod 6, and hence, neglecting friction
5o and weight, the power required for lifting
the driver link equals approximately one-
half of the load carried by the plunger rod
6. Obviously, the ratio of the power and
load may be varied by transferring the
55 pivot 23 to other of the apertures 27, or by
similarly transferring the pivot 11. While
the pivots 18, 19 and 21 were in alinement
the link 8 began to move upward, and this
upward movement was uniformly acceler-
6o ated throughout the first half of its up-
stroke, or throughout the first 90 degrees
travel of the driver crank (not shown), until
said link reached its medial position, which
approximately agrees with the full line posi-
65 tion in Fig. 1. At the beginning of the up-stroke, the pivot 19 begins to move out of
alinement with the pivots 18 and 21, and at
this point the movement of the pivot 21 is
imperceptible, but as the pivot 19 moves later-
ally and downward, the downward movement 70
of the pivot 21 and the upward movement
of the pivot 24 and rod 6 are accelerated. Now
we have seen that the movement of the link
8 is accelerated, and hence the accelerated
movement of the several levers, and this 75
accelerated motion of the link 8 in addition
to the accelerated motion imparted to the
pivot 21 by the laterally downward move-
ment of the pivot 19 approximately doubles
the rate of acceleration of the rod 6 until 80
the driver crank starts into the second quar-
ter of its revolution, whereupon, the upward
motion of the link 8 changes from uniformly
accelerated to uniformly retarded motion
while the motion imparted to the pivot 21 85
by the link 20 and pivot 19 continues to be
uniformly accelerated, or in opposition to
the uniformly retarded motion of the link 8.
It will be seen that these two opposing ac-
celerations of motion counteract each other 90
so as to cause the rod 6 to move with ap-
proximately invariable speed throughout
the upper half of its stroke. It will now be
seen that while the average speed of the rod
6 is only approximately half of that of the 95
rod 7 and link 8, the beginning of the up-
ward movement of said rod 6 is very slow
and becomes very rapidly accelerated until
it attains the approximate average speed of
the link 8. Therefore, the minimum power 100
is required for starting the pump-rod 6 up-
ward, while the usual jerk and jar, which
attains this stage of operation in pumps of
ordinary construction, are reduced to a
minimum. 105
It will, be seen that I have provided a
power transmission mechanism which, while
of simple construction, is fully capable of
attaining the foregoing objects in a thor-
oughly practical and efficient manner. 110
I do not limit my invention to the exact
details of construction, combination and ar-
rangement of parts as herewith illustrated
and described, but my invention may only be
limited by a reasonable interpretation of 115
the claims.
I claim:
1. In a transmission mechanism for con-
necting a pump and a wind mill, an oblique
standard having upper and lower substan- 120
tially horizontal levers pivoted thereto, the
lower lever being adapted for connection
with a wind mill, the upper lever being
adapted to connect with a pump, an oblique
lever pivotally connected to the oblique 125
standard, the obliquity of the oblique lever
being opposite to that of the standard, a
link pivotally connected to said lower lever
and to the oblique lever, and a link pivot-
ally connecting an end of said upper lever 1302
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Reference the current page of this Patent.
Slover, James S. Pump and Windmill Connection, patent, July 22, 1913; [Washington D.C.]. (https://texashistory.unt.edu/ark:/67531/metapth853631/m1/3/: accessed July 18, 2024), University of North Texas Libraries, The Portal to Texas History, https://texashistory.unt.edu; crediting UNT Libraries Government Documents Department.