IMPROVEMENTS IN AND RELATING TO PUMPS AND MACHINERY OR APPARATUS FOR DRIVING OR OPERATING THE SAME
Year: 1880

page_text: LETTERS PATENT to William Robert Lake, of the Firm of Haseltine, Lake,
& Co., Patent Agents, Southampton Buildings, London, for an Invention
of "IMPROVEMENTS IN AND RELATING TO PUMPS AND MACHINERY OR
APPARATUS FOR DRIVING OR OPERATING THE SAME." A communication
from abroad by Pierre Eymard Jay, of the City and State of New York,
United States of America.
PROVISIONAL SPECIFICATION left by the said William Robert Lake at the
Office of the Commissioners of Patents on the 6th October 1880.
WILLIAM ROBERT LAKE, of the Firm of Haseltine, Lake, & Co., Patent Agents,
Southampton Buildings, London. "IMPROVEMENTS IN AND RELATING TO PUMPS
"
AND MACHINERY OR APPARATUS FOR DRIVING OR OPERATING THE SAME."
[A communication from abroad by Pierre Eymard Jay, of the City and State of
New York, United States of America.]
The chief object of this Invention is to provide improved pumping apparatus
and means for driving or operating the same, whereby greater steadiness than
ordinarily exists may be given to the operation of the pump, and whereby the
pump itself may be provided with an efficient packing easily adjustable and readily
accessible without removing the pump connections.
The said Invention comprises certain novel combinations of parts whereby the
aforesaid objects are effectually secured.
In carrying the said Invention into practice I make the pump cylinder in two
parts, the lower part having at its inner extremity a circumferential offset, and
the upper part having at its inner extremity a circumferential flange which fits
upon the flat inner extremity of the offset, and is firmly secured thereto; these
two parts have their interiors bored out for the reception of the plunger. The
diameter of this plunger is somewhat less than the internal diameter of the pump
cylinder, in practice about one sixteenth of an inch, so that a space of about the
one-thirty-second part of an inch is left all around the plunger, between the said
plunger and the adjacent internal surface or bore of the cylinder. Formed inter-
nally within the said offset portion is an annular chamber which receives the
packing, the said packing being of any suitable kind. The bottom of this annular

page_text: chamber is inclined or sloping, the inclination being downward and inward. Above
the packing, and capable to a greater or less degree of a vertical movement within
the aforesaid annular chamber, is a metallic ring, the underside of which is inclined
or sloping in an inward and upward direction. Passed through vertical openings
in the flange of the upper part of the cylinder are movable bolts, by which a
downward pressure may be communicated to the metallic ring. When this is done
the packing acted upon at its opposite sides by the inclined bottom of the annular
chamber, in which the said packing is placed, and the sloping or inclined inner
surface of the ring, is compressed and wedged inward against and around the
plunger, so that the said plunger is kept concentric with the surface of the bore of
the pump cylinder, the slight space between the plunger and said surface being
filled by the inward projection against the plunger of the packing, so that by this
means the plunger is supported around its circumference through only a small
portion of its length by the packing, thereby diminishing the friction exerted upon
the piston as it is moved to and fro within the pump cylinder and through the said
packing. By thus providing a stationary packing capable of being compressed
against the plunger in such a manner that the plunger will move free and out of
all contact with the surface of the cylinder itself, a most effectual packing to the
plunger is secured simultaneously with a very considerable reduction of the friction,
and consequently loss of power, which would otherwise be incident to the move-
ment of the plunger. It may be here remarked that the arrangement of the parts,
such as valves and the like, of the pump may be of any ordinary or suitable kind
adapted to a pump of the general character herein indicated, but the arrangement,
according to this Invention, may be used with very superior results.
The packing may be of hemp or other fibrous material, or it may be composed
of concentric metallic rings, each split at a suitable part in order to permit of its
contraction or expansion as required, and said rings being made to break joint in
the manner well understood. In either case the action of the ring when brought
downward or inward, as herein before explained, is to compress the aforesaid packing
rings and force them radially inward, so to speak, against the adjacent surface of
the plunger to form a tight packing thereto, and to sustain the said plunger con-
centric with the inner surface of the pump cylinder, but out of contact therewith.
The said ring may be operated by having the bolts constructed as set screws working
through suitable nuts tapped in the Hange, in which case the bolts requiring
separate adjustment involve considerable skill and care in their manipulation to
properly operate the ring. To obviate this difficulty a screw thread is formed on
the outer circumference of the aforesaid offset, and a similar screw thread is formed
on the inner portion of the outer circumference of the upper part of the cylinder.
A cap having an internal screw thread screws upon the thread of the upper part;
the said cap is also formed with a downwardly projecting circumferential flange, in
which is formed an internal screw thread which screws upon the thread of the
bottom part of the annular chamber of the cylinder. The movable bolts in this
case are arranged simply to slide through the holes in the flange, and while their
innermost ends rest upon the adjacent surface of the ring their outermost ends rest
against the innermost surface of the cap. By rotating the cap therefore to force
the bolts inward, the ring, acting in conjunction with the sloping bottom of the
annular chamber containing the packing, will cause the said packing to be forced
inward to and against the plunger, as hereiubefore explained, and inasmuch as all
of the bolts will be simultaneously and uniformly acted upon by the inward move-
ment of the cap, it follows that the compression and consequent inward pressure of
the packing will be uniform in character and simultaneous in movement at all parts
of the said packing; in other words, at all parts of the circumference of the plunger.
The ring or cap from its attachment to the two parts of the pump cylinder may be
used as means either alone or in conjunction with other devices for connecting or
holding together the said two parts of the cylinder.
According to my said Invention I also provide a pump barrel or body with
upper and lower portions, to which portions are ordinarily attached the pipes,
E

page_text: one
connections, and the like, of the pump, and which are stationary or permanent.
The inner end of each of the said portions is provided with an internal screw
thread; the central portion of the pump barrel or body is internally threaded
at both ends; this central portion is connected with the upper part by an
end is screwed into the upper
externally threaded section, which at
In like manner the
section, and at the other end into the central section.
central portion is connected with the lower part by another externally threaded
section. The externally threaded sections are of cylindrical form, have the same
internal diameter, and are placed in the same axial line. Apart from the space
occupied by the packing, the externally threaded sections constitute the bore of the
pump. Provided internally to the central portion is an inwardly projecting
circumferential rib, which is wedge shaped, with its upper and lower surfaces
respectively sloping inward. Placed between this rib and the adjacent inner ends
of the externally threaded sections are two rings, the inner surfaces of which
A double
are made sloping at an angle to the adjacent surface of the rib.
packing (or rather two separate packings) is provided by placing a suitable
gasket or packing ring in each of the spaces between the internal rib and the rings,
it being manifest that by turning the externally threaded sections to force their
inner ends inward toward the internal rib the packing will be crowded inward
around and against the circumference of the pump plunger. The externally
threaded sections, and also the central portion, are provided with hexagonal collars,
which may be grasped by a wrench in order to turn the externally threaded
sections, or either of them, with reference to the other parts of the pump barrel.
Jam nuts are provided for making snug the joints between the sections and the
adjacent parts at which they are connected. In order to gain access to the lower
packing it is only necessary to turn the lower sections to screw the same in a
downward direction into the lower part of the pump barrel, which brings the said
section out of and away from the central portion, the internal screw thread of the
central portion being coincident in character and pitch with that of the lower part
aforesaid. By thus bringing downward the lower section sufficient space is pro-
vided to afford access to the lowermost of the packing rings; when it is desired to
have access to the uppermost of the packing rings another section is operated in
like manner,
the said section being in that case screwed upward into the upper
part and out of the central portion. The driving or operating apparatus is con-
structed as follows, that is to say :-
I provide a crank one end of whose shaft is provided with a wheel. This crank
receives its rotary motion from a connecting rod or pitman in the usual manner.
Placed at opposite parts of the circumference of the aforesaid wheel, and at the
front of the same, there are guides. Placed within reach of these guides is a
friction roller which is made in two parts, and each part is provided at its outer
edge with a circumferential flange. These two parts are placed opposite each
other upon an axial pin which passes through a guide, and has its inner end
screwed into the rim of the wheel.
Fixed in front of the wheel are two horizontal guides which may be supported
upon standards, or otherwise made stationary; between these moves a sliding
block, formed in the underside of which is a rack; working in suitable bearings
attached to the lowermost of the guides is a shaft provided with a crank hand-
wheel or the like. Upon the said shaft is a spur pinion, which gears into the rack,
so that by turning the crank more or less the sliding block may be moved
horizontally between the guides, and to any required distance laterally from the
axial line of the crank shaft. In order to retain the block within the guides the
inner side of said block is formed with horizontal flanges at its upper and
lower edges, which bear against the adjacent side surfaces of the guide. Upon the
opposite or front side of the block is placed a flat plate, the upper and lower edges
of which extend upon the adjacent upper and lower side edges of the guides. A
bolt having a head at its inner end passes through the sliding block and the plate,
and-being provided at its outermost end with a screw thread and a nut the plate is

page_text: kept in position so that its upper and lower edges serve the same purpose at the
front of the block as the flanges serve at the back thereof, and by this means the
displacement of the block in a forward or backward direction from the guides is
prevented. Furthermore, by tightening the nut upon the bolt the plate and block
are drawn toward each other, so that the flanges on one side of the guides and the
upper and lower edges of the plate on the other side of said guides are caused to
grip the guides with a force sufficient to hold the block firmly and at any desired
point along the length of the said guides.
The head of the bolt is of cylindrical shape and of such a length as to afford a
bearing for the inner ends of two radial arms, there being an annular flange or
supplemental head formed at the outermost extremity of the bolt head in such a
manner that the inner or pivoted ends of the arms are held between the flange and
the rearmost surface of the block. It is desirable that the bolt should be situated
substantially in the same horizontal plane as the axis of the crank shaft. In the
outermost portion of each of the arms is a slot, and these arms pass within the
guides with the rollers situate within the aforesaid slot. To enable this to be done
the said rollers have the construction herein before explained, the parts being put in
their proper relation by first detaching the guides, then inserting the two parts of
each of the rollers in proper position in the slots, then replacing and securing in
place the guides, and finally passing a pivotable screw through the axial openings of
the parts. Upon the outer extremity of each of the arms is a weight, the ends of
which are tapered to a sharp edge in order that the resistance of the air to the
rotary motion of the weights may be reduced to the least possible degree. The
sharpened ends of the weights divide the air and throw it laterally, thereby
receiving less resistance than would be the case if they were flat or square
across.
The guides are so placed upon the wheel that the arms are in a position at an
angle to the position of the crank upon the shaft, of which the said wheel is
attached.
I further provide a fixed shaft or bearing, to which are pivotted the inner ends:
of two arms which extend in substantially opposite directions, and the outer end of
each of which is pivotted to one side of a sliding weight. These weights slide
upon two oppositely radiating spokes, which may when desired be provided with a
rim to constitute a fly wheel. These spokes extend in opposite directions from a
central hub; this hub works upon a suitable bearing or journal, which is offset
from the shaft or bearing. The spokes are rectangular in their cross-section, and
pass through longitudinal slots of corresponding shape in the weights. In order
that these weights may be properly attached in place upon the spokes, each of the
said weights is made in two parts, that is to say, is composed of two lateral sections
held together by screws. The crank is formed upon or attached to the hub so as
to rotate therewith. When the crank is brought to one of its dead points one of
the weights is projected towards the outer extremity of the spoke upon which it is
placed, and being thereby brought further from the axis of motion of the crank
operates to turn the latter past its dead point. When the crank has reached its
opposite dead point the other of the weights is projected toward the extremity of
the other of the spokes aforesaid, and in like manner carries the crank opposite its
second dead point, and so on, each dead point of the crank being overcome by the
action of a weight projected toward the extremity of its supporting spoke. The
same operation which projects one of the weights toward the outer extremity of its
spoke also moves inward the other weight toward the inner extremity of the 5
opposite spoke. The spokes being of rectangular form in their cross section, and
being passed through slots of corresponding shape in the weights, prevent any
twisting or axial motion of said weights upon the spokes, and thereby prevent
torsion upon the pivots by which the arms are connected with the said weights, and
also prevent a twisting action upon the arms themselves, which in practice would
be extremely detrimental to the operation and durability of the machine. By the
construction herein before specified of the said weights the rectangular slots may be

page_text: very readily formed in the weights, and the weights themselves may be with very
great convenience attached in place to slide upon the spokes. For very light work,
especially when a high speed of the crank is required, only one of the arms with its
attached weight need be used, inasmuch as the velocity required in throwing the
crank opposite one of its dead points will, in the case of light machinery as just
mentioned, be in very many cases sufficient to carry it past the dead centre.
It is to be observed that the connection between the shaft of the engine and the
plunger of the pump may be made in any appropriate or suitable manner, and that
the steadiness and uniformity of movement secured in the engine in its peculiar
construction and its combinations of parts embraced therein insures a corre-
spondingly uniform, certain, and steady operation of the pump.
I employ a valve in a spheroidal valve chest divided by a curved partition, in
which is provided the valve seat, so that a most efficient water way is secured, at
the same time that a proper placing of the valve is provided for.
SPECIFICATION in pursuance of the conditions of the Letters Patent filed by
the said William Robert Lake in the Great Seal Patent Office on the 6th
April 1881.
WILLIAM ROBERT LAKE, of the Firm of Haseltine, Lake, & Co., Patent Agents,
Southampton Buildings, London. "IMPROVEMENTS IN AND RELATING TO PUMPS
AND MACHINERY OR APPARATUS FOR DRIVING OR OPERATING THE SAME."
A communication from abroad by Pierre Eymard Jay, of the City and State of
New York, United States of America.
The object of this Invention is to provide an improved system of pumping
apparatus and means for driving or operating the same, whereby greater steadiness
than is ordinarily obtained may be given to the operation of the pump, and
whereby the pump itself may be provided with an efficient packing which is
easily adjustable and readily accessible without removal of the pump connections.
My said Invention comprises certain novel combinations of parts whereby the
aforesaid objects are effectually secured.
In the accompanying Drawings
Figure 1 is a partial side view and vertical section representing a pump
embodying my said Invention, and
Figure 2 is a vertical longitudinal section of the pump including certain
modifications in my said Invention.
Figure 3 is a vertical longitudinal section of a pump comprising certain other
features of my said Invention, the parts being represented in the position occupied
by them when the pump is ready for use.
Figure 4 is a similar view of the same, but showing some of the parts raised to
afford access to the packing.
Figure 5 is a front view of an inverted vertical steam engine provided with

page_text: devices, also included in my said Invention, for insuring steadiness in the operation
of the pump or other mechanism, to the operation of which the said engine is
applied.
Figure 6 is a front view partly in section of a portion of the same.
Figure 7 is a plan or top view, and
Figure 8, a vertical sectional view taken in a plane at right angles to Figure 6.
Figure 9 is a sectional view illustrating one of the details of construction in
the apparatus shewn in the last named Figures.
Figure 10 is a front view of part of a similar engine including certain
modifications also embraced in the said Invention.
Figure 11 is a plan and partial horizontal section thereof.
Figures 12 and 13 are detail views of one part of the apparatus, as represented
in the last named Figures.
Having reference first to Figures 1 and 2, the pump cylinder is composed of two
parts A and B, the part A having at its inner extremity the circumferential off
set a, and the part B having at its inner extremity a circumferential flange b, which
fits upon the flat inner extremity of the offset a and is firmly secured thereto;
these two parts have their interior bored out for the reception of the plunger C.
The diameter of this plunger C is somewhat less than the internal diameter of the
pump cylinder A, B, (in practice about one sixteenth of an inch), so that a space of
about the one-thirty second part of an inch is left all around the plunger C between
the said plunger and the adjacent internal surface or bore of the cylinder. Formed
internally within the offset portion a of the part A of the pump cylinder is an
annular chamber which receives the packing D, the said packing being of any
suitable kind, as hereinafter more fully explained. The bottom c of this annular
chamber is inclined or sloping, the inclination being downward and inward, as
represented in the Drawings. Above the packing D, and capable of a greater or
less degree of vertical movement within the aforesaid aunular chamber, is a
metallic-ring f, the underside of which is inclined or sloping in an inward and
upward direction, as also represented in the Drawings. Passing through vertical
openings in the flange b of the part B of the cylinder are movable bolts g, by
which a downward pressure may be communicated to the ring f. When this is
done the packing D acted upon at its opposite sides by the inclined bottom c of
the annular chamber in which the said packing is placed, and the sloping or
inclined inner surface of the ring f is compressed and wedged inward against and
around the plunger C, so that the said plunger is kept concentric with the surface
of the bore of the pump cylinder, the slight space between the plunger and the
said surface being filled by the inward projection against the plunger of the
packing D, so that by this means the plunger is supported around its circumference
through only a small portion of its length by the packing, thereby materially
diminishing the friction exerted upon the piston as it is moved to and fro within
the pump cylinder and through the said packing. By thus providing a stationary
packing capable of being compressed against the plunger in such a manner that the
plunger will move freely and out of all contact with the surface of the cylinder
itself, a most effectual packing to the plunger is secured simultaneously with a
very considerable reduction of the friction and consequent loss of power, which
would otherwise be incident to the movement of the plunger. It may be here
remarked that the arrangement of the ports, valves, and other parts of the
pump may be of any ordinary or suitable kind adapted to a pump of the general
character, herein indicated, or that represented in the Drawings, may be used with
very superior results.
The packing D inay be of hemp or fibrous material, as represented in Figure 1,
or it may be composed of concentric metallic rings each split at a suitable part, in
order to permit of its contraction or expansion as required, the said rings being
made to break joint in the manner well understood by mechanics conversant with
the packing of pumps, engines, and the like. In either case the action of the ring f
when brought downward or inward, as hereinbefore explained, is to compress the

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page_text: and the portion C₁ is also hexagonal, so that they may be grasped by a wrench in
order to turn the sections E¹, F', or either of them, with reference to the other
parts of the pump barrel, as herein presently explained. Placed upon the threaded
exterior of the section E¹ are jam nuts E, E, and in like manner upon the
threaded exterior of the section F1 are placed similar jam nuts F, F, the use
and object of which are to provide for making snug the joints between the
sections E, F, and the adjacents parts to which they are connected, as herein before
explained. In order to gain access to the lower packing f¹ it is only necessary to
turn the lower section F' to screw the same in a downward direction into the
lower part B¹ of the pump barrel, which brings the said section F' out of and away
from the central portion C¹, the internal screw thread of the central portion C¹
being coincident in character and pitch with that of the part B¹ aforesaid. By thus
bringing downward the lower section F1 sufficient space is provided to afford access
to the lowermost of the packing rings f¹, which space may be further increased by
screwing the upper section E¹ upward into the part A¹ when it is desired to have
access to the uppermost of the packing rings. The section E is operated in like
manner, the said section E¹ being in that case screwed upward into the part A' and
out of the central portion C¹. It is understood that in thus manipulating either
the section E¹ or the section F' the jam nut E or F", as the case may be, is
screwed as far as possible away from the outer end of the section to be moved, the
outer ends of the jam nuts E", E, and F", F, being simply to hold snugly
against the ends of the two sections E¹, F1, and of the central portion C¹
respectively, when the parts are in position for the use of the pump, and also to
render more tight and snug the joints between the central portion and the
sections E', F', and those between the sections E, F, and the upper and lower parts
of A', B¹.
It will be particularly observed that by my aforesaid Invention all the effects of
expansion and contraction caused by change of temperature in the pump barrels
are provided against, inasmuch as the packing is readily compressed to any required
degree against the plunger, and any expansion which would vary the vertical width
of the receptacles of the packing is thereby easily compensated for. It will be
further understood, by reference to the Drawings, that the plunger being of less
diameter than the bore of the pump barrel there is no friction whatever except
where the two packing rings come in contact with the plunger, and that this
friction is only proportioned to the pressure with which the packing is forced
inward against the plunger by the operation of the sections, as hereinbefore
explained.
Having reference now to Figures 5, 6, 7, 8, and 9, A³ is the crank, of which the
axial shaft is shown at B3, one end of the said shaft being provided with a wheel C³,
the purpose of which will hereinafter appear. In the Drawings the crank A³ is
shown in Figure 5 at the upper dead centre, and in Figures 6 and 8 at the lower
dead centre. The crank receives its rotary motion from the connecting rod or
pitman D in the usual manner. Placed at opposite points of the circumference of
the wheel C³, at the front of the said wheel, as more clearly represented in Figures 5
and 6, are guides E³, the construction of which is indicated in detail in Figure 9.
Placed within each of these guides is a friction roller a³, which is made in two
parts a¹, each part provided at its outer edge with a circumferential flange c¹; these
two parts are placed opposite each other upon an axial pin 63, which passes
through the guide E³, and has its inner end screwed into the rim of the
wheel C³.
Fixed in front of the wheel C³ are two horizontal guides F³, which may be
supported upon standards G³, or otherwise made stationary; between these bars.
moves a sliding block H³, formed in the under side of which is a rack c³, represented
in dotted outline in Figures 5 and 7 and also shewn in Figure 8. Working in
suitable bearings attached to the lowermost of the guides F3 is a shaft d³, provided
with a crank, hand-wheel, or the like, as at e³. Upon the said shaft d³ is a spur
pinion ³, which gears into the rack, so that by turning the crank e³ more or less

page_text: the sliding block H³ may be moved horizontally between the guides F3, and to any
required distance laterally from the axial line of the crank shaft B³, in other words
from the line of the axis of rotation of the crank A³. It should be mentioned that
in order to retain the block H³ within the guides F3 the inner side of the said
block is formed with horizontal flanges at its upper and lower edges which
bear against the adjacent side surfaces of the guides F³. Upon the opposite or
front side of the block H³ is placed a flat plate h³, the upper and lower edges of
which extend upon the adjacent upper and lower side edges of the guides F³; a
bolt 13, having a head is at its inner end, passes through the block H³ and plate h³,
as represented in Figure 8, and being provided at its outermost end with a screw
thread c' and a nut m³. The plate h³ is kept in position so that its upper and lower
edges serve the same purpose at the front of the block H³ as the flanges g³ serve at
the back thereof, and by this means the displacement of the block H³ in a forward
or backward direction from the guides F³ is prevented. Furthermore, by tightening
the nut m³ upon the bolt I³, the plate and block H are drawn toward each
other, so that the flanges g³ on one side of the guides F³, and the upper and lower
edges of the plate hs on the other side of said guides are caused to grip the guides
with a force sufficient to hold the block H³ firmly and at any desired point along
the length of the said guides.
The head 3, of the bolt 13, is of cylindrical shape, and of such a length as to
afford a bearing for the inner ends of two radial arms K³, there being an annular
flange or supplemental head n³, formed at the outermost extremity of the head 2³
in such a manner that the inner or pivoted ends of the arms K³ are held between
the flange n³ and the rearmost surface of the block H³, as more clearly represented
in Figure 8. It is desirable that the bolt 13 should be situated substantially in the
same horizontal plane as the axis of the crank shaft B³. In the outermost portion
of each of the arms K³ is a slot ³; these arms K³ pass within the guides E³ with
the rollers a situate within the aforesaid slot r³. To enable this to be done the
said rollers a³ have the construction hereinbefore explained, the parts being put in
their proper relation by first detaching the.guides E³, then inserting the two parts
a of each of the rollers a³ in proper position in the slots, then replacing and
securing in place the guides E3, and finally passing the pivotal screw 63 through
the axial openings of the parts a¹. It will be observed that the guides E³ serve to
retain the rollers as in position, and that the said rollers a³, together with the
flanges thereof, hold the arms K³ against displacement, and at the same time
reduce to a minimum the friction incident to the longitudinal movement of the
said arms through the said guides as hereinafter explained; the said longitudinal
movement being permitted by the slot in the said arms K³. Upon the outer
extremity of each of the arms K³ is a weight L³, the ends of which are tapered
to a sharp edge in order that the resistance of the air to the rotary motion, herein-
after described, of the weights L³ may be reduced to the least possible degree; the
sharpened ends of the weights L³ divide the air, throwing it laterally, thereby
receiving less resistance than would be the case if they were flat or square across.
The guides E3 are so placed upon the wheel C³ that the arms K³ are in a position
at an angle to the position of the crank A³ upon the shaft B³, to which the said
wheel C is attached, as hereinbefore explained. In order to put the apparatus in
operation, the block H³ is moved laterally to bring the axis of the bolt Is, in other
words, the axis of motion of the arms K³, to a greater or less distance from the
axial line of the crank shaft B³, in other words, to make the path of rotation
of the weights L³ eccentric to the path of rotation of the wheel C³. This being
done the block H³ is tightened in place as hereinbefore explained. The crank being
put in rotation by the movement of the pitman or connecting rod D³, it follows
that the rotation of the wheel C³ will revolve the arms K³, and consequently their
weights L3; and inasmuch as the axis of motion of the latter is eccentric to that of
the said wheel Cs, it follows that as each of the arms K³ is turned over toward that
side of the wheel to which the axis of rotation of the arm is nearest, the said arm
will change its position with reference to the circumference of the wheel, being

page_text: thrust out therefrom to an extent equal to twice the distance of the axial line
of rotation of the arm from that of the wheel C³. By this means the weight
on the arm K³ is carried to a greater distance from the axis of the wheel C³,
and being thereby caused to preponderate at that side of the wheel, depresses the
said side of the said wheel during a portion of its revolution. Furthermore, the
two weights being simultaneously moved when one weight is protruded from one
side of the wheel, the other weight is drawn inward at the opposite side of the
wheel, and as this occurs as each weight is brought in succession toward and to
one side of the wheel, as just explained, and as this preponderating action of the
weights at one side of the wheel C³ is made to coincide in point of time with the
dead points of the crank, it follows that when the pitman is powerless to act upon
the crank, as is always the case at the dead points, the preponderance of the weight
at one side of the wheel ensures the rotation of the latter, and consequently the
rotation of the crank shaft and the throwing of the crank A³ past the dead points.
It is to be understood that one of the arms K³ with its weight L³ answers to one
of the dead points of the crank, while the other arm and its weight answers to the
other dead point of the crank, so that by these means it is impossible to have the
crank remain upon the dead point, inasmuch as when the action of the pitman or
connecting rod ceases upon the crank, the action of one or the other of the weights
is brought into play to throw the crank past the dead point, at which the pitman
or connecting rod is idle, and as the extent of the throw of the weights L³ is regu-
lated by the distance between the axial line of rotation of the arms K³ and the
axial line of the crank shaft B³, the intensity of the force exerted to turn the
crank past its dead points may be adjusted with great readiness and delicacy by
the lateral adjustment of the block H³, as hereinbefore explained.
Having reference to Figures 10, 11, 12, and 13, B5 is a fixed shaft or bearing to
which are pivoted the inner ends of two arms K³ which extend in substantially
opposite directions, and the outer end of each of which is pivoted to one side of a
sliding weight L³, as represented at 6 in Figure 11, and also in dotted outline in
Figure 10. These weights slide upon two oppositely radiating spokes c*, which
may, when desired, be provided with a rim I' to constitute a fly wheel. These
spokes c extend in opposite directions from a central hub f; this hub works upon
a suitable bearing or journal 9 which is offset from the shaft or bearing B³, as
indicated in Figure 11, in other words, the axis of the bearing on which the hub f
rotates is situated at some distance from and parallel with the axis of the shaft B*
on which the inner ends of the arms K³ are pivoted, as hereinbefore explained.
The spokes care rectangular in cross section, as represented in Figures 12 and 13,
and pass through longitudinal slots of corresponding shape in the weights L³. In
order that these weights may be properly attached in place upon the spokes c¹,
each of the said weights is made in two parts, that is to say, is composed of two
lateral sections held together by screws n, as represented in Figures 12 and 13.
The crank is shewn at A³, and is formed upon or attached to the hub f so as to
rotate therewith. When the crank is brought to one of its dead points one of the
weights is projected towards the outer extremity of the spoke upon which it is
placed, and being thereby brought further from the axis of motion of the crank
operates to turn the latter past its dead point. When the crank has reached its
opposite dead point the other weight is projected toward the extremity of the
other spoke aforesaid, and in like manner carries the crank opposite its second
dead point, and so on, each dead point of the crank being overcome by the action
of a weight projected toward the extremity of its supporting spoke. The same
operation which projects one of the weights toward the outer extremity of its spoke
also moves inward the other weight toward the inner extremity of the opposite
spoke. The spokes being of rectangular form in their cross section, and being
passed through slots of corresponding shape in the weights L³ prevent any twisting
or axial motion of the said weights upon the spokes, and thereby prevent torsion
upon the pivots by which the armis K³ are connected with the said weights, and
also prevent a twisting action upon the arms themselves, which in practice would

page_text: be extremely detrimental to the operation and durability of the machine. By the
construction (herein before specified) of the said weights L³, the rectangular slots
may be very readily formed in the weights, and the weights themselves may be,
with very great convenience, attached in place to slide upon the spokes. For very
light work, especially when a high speed of the crank is required, only one of the
arms Ks with its attached weight L³ need be used, as the velocity required in
throwing the crank opposite one of its dead points will, in the case of light
machinery, as just mentioned, be, in very many cases, sufficient to carry it past the
dead centres.
It is to be observed that the connection between the shaft of the engine and the
plunger of the pump may be made in any appropriate or suitable manner, and that
the steadiness and uniformity of movement secured in the engine in its peculiar
corre-
construction, and its combinations of parts embraced therein ensure a
It is also to be
spondingly uniform, certain, and steady operation of the pump.
observed that a most useful construction of valve for the pump is that represented
at the left hand side of Figures 3 and 4, the spheroidal valve chest A being sub-
divided by the curved partition a, in which is provided the valve seat, so that a most
efficient water way is secured at the same time that a proper placing of the valve
is provided for.
Having thus fully described the said Invention, as communicated to me by my
foreign correspondent, and the manner of performing the same, I wish it understood
that I claim,
First. The combination of the offset a having the sloping bottom c, the ring f
having its inner side inclined or sloping in a direction opposite to the inclination of
the bottom c, the packing D interposed between the aforesaid ring f and the
sloping bottom c, the bolts g for actuating the ring f, and the plunger C, having
a diameter somewhat less than the bore of the pump cylinder in which it is placed,
all substantially as and for the purpose herein set forth.
Second. The ring E constructed with the screw threads in combination with the
screw thread of the part A of the cylinder, the screw thread of the part B of tho
said cylinder, the sloping or inclined bottom c of the offset a, the packing D,
the ring f, and movable bolts g, substantially as and for the purpose herein set
forth.
Third. The pump cylinder composed of the part A having the offset a, and the
part B having the flange b, whereby when the parts are joined an annular chamber
is formed for the reception of a stationary packing, substantially as and for the
purpose herein set forth.
Fourth. A pump body or barrel constructed with one or more screwed sections,
capable of longitudinal adjustment to afford access to the interior of the said barrel,
substantially as and for the purpose herein set forth.
Fifth. In a pump barrel the combination of the internally screw threaded end
parts A and B', the externally screw threaded sections E' and F', the internally
screw threaded central portion C" carrying a suitable packing, and a plunger D',
all substantially as and for the purposes herein set forth.
Sixth. The internally threaded central portion C' constructed with the internal
circumferential rib c¹, the two packing rings e', f', the externally threaded sections
E, F, the internally threaded end parts A, B, and the piston D', all substantially
as and for the purpose herein set forth.
Seventh. The combination of the jam nuts F", F, and E", E¹¹, with the
internally threaded end parts A', B', the externally threaded sections E¹, F', and
the internally threaded central portion C¹ of the barrel, all substantially as and for
the purpose herein set forth.
Eighth. The combination of the laterally adjustable block H³ carrying the pivot
of the arms K³, provided at their outer extremities with weights L³, the wheels C³
having guides for holding the arms K³ in position, and the crank A³ having the
wheel attached to its shaft B³, all substantially as and for the purpose herein set
forth.

page_text: Ninth. The combination of the laterally adjustable block H³, plate h³, bolt I³,
nut m³, guides F³, pivoted arms K³ having weights L³, wheel C³ having guides for
retaining the arms K³ in position, and crank A³, the whole arranged for joint use
and operation, substantially as and for the purpose herein set forth.
Tenth. The combination of the block H³ having the rack c³ on its underside,
and a pinion f having a crank or hand wheel, in combination with the arms K³
having weights L³, the wheel C³ having guides for holding the arm K³ in position,
and the crank A³, there with arranged for joint use and operation, substantially as
and for the purpose herein set forth.
Eleventh. The rollers a³, each composed of the two parts a', having the flanges c¹,
the guides E3, and pivots or screws b³, in combination with the slotted arms K³
having weights L³, the wheel C³, and the crank, all substantially as and for the
purpose herein set forth.
Twelfth. The weights L³ constructed with sharpened ends, as described, in
combination with the arms K³ and the wheel C³ on the shaft of the crank A³, all
substantially as and for the purpose herein set forth.
Thirteenth. A spoke or spokes c* having a rectangular cross-section in combi-
nation with a weight or weights L³, bearing B5, bearing g', and arm or arms K³,
all substantially as and for the purpose herein set forth.
Fourteenth. A weight or weights L³ composed of lateral sections 7, secured
together by screws or bolts n, in combination with a radial spoke or spokes c¹,
bearing B5, bearing g, and radial arm or arms K³, all substantially as and for the
purpose herein set forth.
In witness whereof, I, the said William Robert Lake, have hereunto set my
hand and seal, this Fifth day of April, in the year of our Lord One
thousand eight hundred and eighty one.
W. ROB, LAKE. (L.S.)