IMPROVEMENTS IN FLUID METERS
Year: 1885

page_text: I PHILIP MIDDLETON JUSTICE of 55 and 56 Chancery Lane in the County of
Middlesex Fellow of the Institute of Patent Agents do hereby declare the nature
of said invention for "IMPROVEMENTS IN FLUID METERS" a communication to me
from abroad by John Thomson of Brooklyn in the County of Kings and State of
New York, United States of America Engineer and in what manner the same is to
be performed, to be particularly described and ascertained in and by the following
statement:-'
This Invention relates to fluid meters of that class in which the displacement is
obtained by the combination of a piston and diaphragm and a valve system. In
general terms the object of the invention, is to improve the operation and mechanical
construction of fluid measuring instruments to reduce the cost of their manufacture;
to produce an instrument which in its working parts shall approximate perfect
equilibrium; requiring less power to operate, being more accurate in its measure-
ments at all flows and pressures, and more durable under long and severe service
than fluid measuring instruments heretofore produced.
More particularly stated, the invention refers to the following special features.
First. The adaptation of the valve actuating apparatus, the valve, piston rod, and
register actuating apparatus to a single separate "form" or base, which, when
entirely completed and assembled is placed and secured within the cylinder, much
as a watch or clock movement is placed within its case.
Second. In an improved construction of the valves, valve chamber, valve spindle,
and valve spring.
"
Third. In an improved arrangement of the valve actuating apparatus.
Fourth. In an improved arrangement for transmitting the sum of the strokes of
the piston to the register.
Fifth. In an improved mode of connecting the register.
Sixth. In an improved means of securing the diaphragm to the cylinder and
piston, and method of assembling the component parts of the same..
Seventh. In an improved manner of forming and constructing the piston.
Eighth. In an improved form of pressure cones.
Ninth. In an improved form of cylinder or case,

page_text: Tenth. In the water ways, sluices and ports the formation being such as to
establish as perfect and complete equilibrium in the operation of the valve and
piston under hydro-dynamic conditions as under hydro-static conditions.
Eleventh. The formation of said water ways and sluices," so as to offer the
minimum of frictional resistance to the flow of fluids.
Twelfth. In the manner of constructing the water ways.
Thirteenth. In an improved positive valve actuating mechanism, whereby the
said valve is thrown with such rapidity of movement, that no appreciable loss of
fluid can occur during the transit of the valve, and also whereby there can be no
increased travel of the piston at fast flows.
Fourteenth. In further constructions, arrangements and combinations of parts as
more particularly pointed out hereafter.
In the accompanying drawings
Fig 1 is an upright cross section of one form of the improved meter, exposing
the valve casing, and valve actuating apparatus in front elevation. Fig 2 is a top-
plan view of the valve casing and its appurtenances. Fig 3 is an upright end
elevation of the valve casing as viewed from the right hand side of Fig 2. Fig 4
is a transverse section through the valve casing on the line C of Fig 2. Figs 5
and 6 are detached. views of the valve. Fig 7 is a detached side elevation, of the
diaphragm and clamping rings. Figures 8 and 9 are detached views of the piston
and clamping ring and Fig 10 is a side plan view of the carriage. Fig 11 is a
vertical central cross section through the cylinder of another form of the improved
meter, exposing the valve casing and the valve actuating mechanism in side
elevation Fig 12 is a top plan view of valve casing and valve actunting mechanism.
Fig 12 is a diagram of valve retaining spring Fig 13 is an upright central cross
section through the cylinders, exposing the valve casing and valve actuating
mechanism in front elevation as viewed from the left hand side of Fig 11. Fig 14
is a central cross section of valve casing on the line A of Fig 12 showing the valve
in its alternative position. Figures 15 and 16 are detached views enlarged of the
valve and valve spindle Fig 17 is a detached view of internal valve seat and
modifications of the same. Fig 18 is a horizontal section through the water ways
and valve casing on the line C of Fig 11 as viewed from below with the operative
mechanism removed. Fig 19 is a detached elevation in partial section of the
pressure cones. Fig 20 is a detached view of piston. Fig 21 is a central vertical
section, through the ingress and egress openings of the cylinder, the sluice ring,
valve chamber and valve. Fig 22 is a horizontal section on line B of Fig 21 as
viewed from above. Fig 23 is a central vertical section on line C Fig 22 exposing
the intermediate water ways in cylinder sluice ring and valve chamber. Fig 24 is
a plan of the upper cylinder as viewed from below, with the sluice ring and valve
chamber in position. Fig 25 is a side elevation of valve chamber and valve Fig 26
is a front elevation of valve actuating apparatus with valve in longitudinal section
and one side of valve chamber removed Fig 27 is a central horizontal section of
valve and valve chamber. I will first describe the apparatus illustrated in Figs 1
to 10.inclusive.
In the construction of apparata of this class heretofore, the practice has
uniformly been, so far as possible, to form the valve casing and every portion
necessary to operate, as a part of the main cylinder or cylinders. These objections
I have found in so far as this precedent has been followed, are, that it is practically
impossible to combine the highest efficiency; the best disposition.of parts within
the smallest space with the least quantity of material, and the lowest cost to
construct the component parts and to assemble the same. The reasons for the
enumerated objections are, that the work to be done is generally within a
cylinder inconvenient and difficult of access or on a cumbrous "bonnet chest or
septum likewise inconvenient to handle. I obviate these difficulties in the
following manner.
The machine work to be done on the lower cylinder 1 and the upper cylinder 2
of the figure consists of drilling the bolt holes 3, bearing for stuffing box 4 and

page_text: binding screws 5 and boring the taper 6. Aside from fitting the ingress and
egress pipes this is the sum of the machine work on the cylinders. To the taper of
the crown of the cylinder is fitted what will be herein termed the valve case 7 in
which is formed a complete system of sluices or water ways, connecting with
corresponding water ways in the cylinder, and to which every working part of the
meter is attached or connected. All of the operations upon the valve casing,
however are performed before it is secured within the cylinder: its attachment
thereto being effected as to position by the register shaft and as to retention by the
screws 5. It will be observed that these screws also serve to force the two tapering
bearing surfaces 6 of the valve casing and cylinder together with great intimacy,
thus making a fluid tight joint between them.
The position of the register shaft bearing is such that it so locates the valve
casing that the egress sluices 9. Fig 2 meets a corresponding cored water way, and
the ingress sluice 10 and intermediate sluice 11 also meets corresponding water
ways in the opposite side of the cylinder.
The intermediate water way 12 (dotted lines Fig 1) of the upper cylinder,
follows down, and meets a corresponding water way 13 in the lower cylinder thus
completing the circuit. The diaphragm 14 is secured between the flanges of the
cylinders, and to the piston 15 (in a manner to be hereinafter described) thus
forming two compartiments within the cylinder; an upper 16, and a lower 17.
The valve is of the compound puppet type and is balanced as to hydrostatic and
working" pressure. By "working" pressure being meant that due to the friction
developed in operating the meter.
The passage of the fluid during the time in which the valve is in the position
shown in Figures 1. 2 and 3 is as follows:-
First. from the ingress sluice 10 to and through the induction port 18 (induction
port 19 and eduction port 20 being closed by the valve 21, 22 and ports 19
and 23 communicating directly with the upper chamber 16), to the intermediate
sluice 11 and water way 12 down to lower compartment 17, thus forcing piston
and diaphragm up, as see dotted outline, and expelling the fluid from the upper
compartment 16 which had previously been filled through the port 19 when the
valve was in the position shown in Fig 14 into and through eduction port 23, to
the egress sluice 24 and thence out. Meantime the piston rod 25 will have made
contact with the arm of the bell crank 26 (Fig 3) through the medium of the pin 27
which projects through the piston rod and also with the register arm 50 which
connects by means of the pin 28 with the piston rod bringing both of said parts to
their alternate position indicated by centre lines Fig 3. In the bell crank the
effect will be to force over the spring carriage 29 against the tension of the
V toggle springs 30 whose thrust is exerted against the thrust block 31 to
the valves thus holding the valves to their seats until the "heels" of said springs-
that is their outer bearings in the spring carriage-will have been carried beyond
their dead centre when they will act to set the valve to its reversed position. The
bell crank is permitted a certain amount of lost motion" in order to set the
springs quickly from off their dead centre. The motion of the bell-crank is limited
by the impact of the pin 27 against the stop shoulders 32 formed in the bearings
of the piston rod.. The position of the valve as now assumed is shown in Fig 4
when the ingress current will flow through the now open induction port 19 directly
into the upper chamber 16 and the fluid free from the lower chamber will be forced
back through the intermediate water way of the cylinder to the intermediate sluice,
of the valve chamber, through the eduction port 20 to the egress sluice of the valve
casing and thence out. The use of the bell crank permits, first, a horizontal
position to the valve, and, second a direct connection with the piston rod and motor
springs actuating the valve.
"
The spring carriage is attached to the bell crank by small pivots, as 33, so that
aid carriage takes the entire direct thrust of the springs, and relieves the bell
rank of the friction of their thrust.

page_text: It will be understood that the angle subtended by the bell crank in its alternate
positions is not transmitted to the carriage and springs as the pivoted connection
permits the carriage to travel back and forth in a vertical line only. In thus directly
connecting the spring carriage to the bell crank, there is thereby developed a
slight error of movement, in that the are described by the bell crank is imparted
to the carriage, and tends to slightly cramp the springs by alternately raising and
lowering their "heels" in their horizontal plane. To eliminate the objection
noted, the springs are formed as shown in Figs 1 and 3, their centre or V portions 30
being considerably. narrower than their bearing surfaces. The effect of this is to
make the springs very elastic horizontally as well as when compressed upon them-
selves; thus their "heels" may be lifted and lowered within the limits required
without interfering with their proper action, besides which. long and durable
bearing surfaces are provided for the knife edge bearings to act upon.
While the carriage might readily be made solid it is preferably built up by the
yokes 33a and bearing blocks 34 as in this way the blocks can be formed in long
pieces with the V bearings 35, accurately milled, and then cut to required length,
while the yokes are stamped from sheet metal. The yokes as will be seen, also
prevent the springs from shifting up or down in their bearings.
The face plates 36 are approximate duplicates each of the other, and are secured
to the valve casing by the screws 38. They form the outer valve seats and also
the bearings in which the valve-spindle 37 operates.
27
In forming the "seats for said face-plates, and also the valve seats 39. 40, (see
Fig 4) of induction and eduction ports, the casing is cast with the annular ribs xx
and chambers and the method of finishing is as follows; A milling tool of the exact
shape required, bores the eduction and induction ports 18. 20 and at the same time
forms a seat for the valve and the face plate 41 on the one side of the valve casing,
The operation is repeated on the opposite side, the bore being continued until the
opposing surfaces are brought to any predetermined distance apart. Thus the face
plates and bearings for the valve are brought exactly central with the ports and
whatever departure there may be from exact truth in the relative vertical planes of
the valve seats, and face plates-as say from the right angle subtended by the
longitudinal centre of the valve stem to the bearing of the bell crank-it will not
materially interfere with the free and proper action of the different parts besides
which the operations are few and simple.
'
•
To reduce the fitting and cost of the valves to a minimum and to adapt the
meter for correct operation in the most severe service-as the measurement of
water charged with grit and impurities, I form a flexile "built up" valve in the
following manner, as see Figs 4 and 5. On the sleeve 42 two hubs 43 are formed
the required distance apart. A portion of the ends of said sleeve are threaded to
receive the binding nuts 44 and the sleeve itself is finished to a length as much less
than the distance between the inner surfaces of the hubs 45 of the face plates as
the full distance of the stroke of the valve. The valve spindle is formed of regular
guage wire forced tightly through the sleeve. Each movement of the valve spindle
will thus cause an alternate end of the sleeve to impinge upon one or other of the
inner surfaces of the hubs 45 of the face plates. Each portion of the valve is then
made up of three plain discs, the first 46 being of leather, vulcanized rubber, or any
suitable analogous material; the second interposed disc-47 being of thin spring
metal; and the third 48 a duplicate of the first. All are then clamped on the
sleeve against the hub by nut as shown. The function of the stops formed by the
ends of the sleeve is now apparent, namely to take the full force of the valve
motor springs 30 and just permit the valve to make proper contact on its seats.
In the event however of any error in the construction of the parts or of a foreign
obstruction being caught between the valve and its seats as illustrated in Fig 6, the
full force of the motor springs will be exerted upon the valve to bring it to a seat
until finally arrested in its movement by the stop. Hence in consequence of the
greater power of the valve motor springs, and the flexile and elastic nature of
the valve, an approximately accurate contact is effected upon the valve seat, under

page_text: conditions that would otherwise render the instrument very inaccurate in its
measurements or totally inoperative..
To effect the registration of the strokes of meters and thereby measure the volume
of liquid displaced, the usual practice heretofore, has been to make direct and
continuous connection whereby each stroke or unit of displacement is transmitted
to the register. The objection to this is that inasmuch as in the smaller sizes of
instruments it requires a number of movements to displace whatever arbitrary unit
of measurement may be adopted as a cubic foot, gallon or litre, and that as the
register is connected by a shaft passing through a packed bearing, the friction is
considerable, and there is liability of leakage through the said packed bearing in
consequence of the frequent movements imparted to the shaft. I obviate these
objections by transmitting to the register by means of the register shaft the result
or sum total only of the movements required to make up a cubic foot or any
arbitrary volume, upon the completion of the movements required to make the sum
of the displacement desired to be indicated. To this end my arrangement is as
follows. On a fixed bearing 49 of the valve casing is mounted the register arm 50
carrying a pawl 51 and a ratchet wheel 52, having one or more projecting pins 53,
said pins being caused to pass in proper pitch line to intermesh with the pin
wheel 54. The said pin wheel is fast to the register shaft 8, mounted in another
fixed bearing 55 of the valve casing. Hence it is apparent, that by a proper
relation of the number of teeth in the ratchet wheel to the piston strokes required
to measure any arbitrary unit of volume a single pin or any one of a number of
pins 53 will be caused to engage a tooth of the pin wheel only at the termination
of a series of piston strokes; and that-the pin wheel will be thus rotated a space
equal to the pitch of one of its teeth; which movement being transmitted to the
register should indicate a full unit of displacement. In the present instance the
adaptation is made with special reference to differential registers in which each full
unit of the dial corresponds to a single tooth of the dial carrying wheel. I therefore
simply attach a pinion as 56 to the upper and outer portion of the register shaft,
which has a number of leaves corresponding to the number of teeth in the pin
wheel 54. Thus each movement of the pin wheel equal to the pitch of its teeth or
pins will rotate the pinion through a space equal to the pitch of its leaves and will
tbus record a complete unit on the register. Supposing therefore that the number
of piston strokes to a cubic foot of fluid is 16, the number of teeth in the pin
wheel 10, and a corresponding number of leaves in the pinion, it would therefore
require, 160 piston movements (16 x 10 = 160) to turn the register shaft one
complete revolution.
The usual manner of securing the diaphragm to the cylinder is simply to clamp
it between the flanges, I have found this objectionable in' that the diaphragm is
subjected to greater pressure by the flange bolts, tending to crush, cut, and squeeze
out the diaphragm, besides bringing it in contact with corrosive metal.
I therefore attach the base of the diaphragm to a pair of non corrosive metal
The
rings 61. 62 the ring 62 fitting snugly within the flange 63 of the ring 61.
diaphragm is then pinched between these rings, and the two rings, as one are placed
in a groove or recess 64 formed in the flange of the upper cylinder, said groove
being of such depth, that the rings and diaphragm are clamped sufficiently tight to
just ensure the diaphragm against withdrawal and to form a watertight joint. The
inner edges 65 of the rings are slightly rounded and the rings project within the
cylinder hence the diaphragm rolls within the fluid completely free from any
disturbing or corrosive influence.
In somewhat like manner I also secure the diaphragm to the piston.
In this
instance, however it becomes desirable to make the piston 15 of the least possible
weight and the greatest stiffness in its horizontal plane to resist buckling or
diaphragmatic action. To this end the piston, see Figs 7. 8 and 9 is formed of
light sheet metal with a rounded outer flange 66, a raised annulus 67 within the
flange, and between the centre bearing, for the piston rod and said annulus 67 are
stamped a number of ribs all of which are tangent to a common circle. concentric.

page_text: with that of the annulus 67 It will thus be seen that in whatever direction the
strain may be applied, as at the lines 68. 69, the said ribs will present a cross
*sectional resistance to the strain or strains, with obvious results.
The ribs may be curved or serpentine instead of straight. The clamping ring 70
Fig 9 is formed with a rounded flange like the piston, and an inner raised
annulus 71. the latter however being turned in an opposite direction to that of the
annulus 67 in the piston. The reason for this is that the piston and the clamping
ring lie one within the other and are thereby accurately centred to each other,
when it simply remains to secure the two together upon the diaphragm to complete
the work.
The mode of setting up or assembling the outer clamping rings and piston is as
follows. In Fig 7. assuine the piston, in dotted outline to be fixed to a jig or
forin" of the exact shape of the inner surface of the diaphragm.
"
Then place the diaphragm upon the form. Next the outer ring over the
diaphragm, the said ring being also secured in a separate "form" of the exact
shape of the outer surface of the diaphragm. The piston, diaphragm, and outer ring
are then virtually locked together as one part It simply remains to drive the inner
ring 62 snugly home to its position within the flange of the outer ring, thereby
stretching the diaphragm and securing it at its base. Then secure the clamping
ring 71 to the piston, as set forth, when the work is completed, and the "forms
may be withdrawn. This mode also ensures uniformity of volume in manufacturing
without after adjustment.
It will be observed that in the flange of the upper cylinder, a downwardly pro-
jecting collar is formed at its outer circumference, and that the flange of the lower
cylinder is formed to fit this collar: The object of this construction is twofold,
first to centre the two cylinders one upon the other and, second to prevent the
packing from being blown out from between the two surfaces of the flanges.
Constructed in this manner the packing may be of such fibrous or plastic material
as to ensure a perfect joint however rough may be the surfaces of the flanges, and
which obviously will be ensured against ejection outwardly without being pinched
excessively by the flange bolts This construction furthermore obviates machining
the flanges of either cylinder (as may have been previously inferred) the castings
being used in the condition received from the mold.
Of course the same results would be obtained by forming the collar on the lower
cylinder. Although I have illustrated the outer meter casing as consisting of two
connected cylinders, the same may be of any suitable construction, and the valve
casing supporting all the operating parts whatever may be their character may be
secured detachably within the outer casing in any suitable manner.
I will now describe those features of my invention which refer more particularly
to the construction and arrangement of the water ways, sluices and ports and
co-operating parts whereby I am enabled to establish as perfect and complete
equilibrium in the operation of the valve and piston, under hydro-dynamic as
under hydrostatic conditions with special reference to the instrument illustrated in
Figs 11 to 20 inclusive.
In order to produce an accurate measuring and durable liquid meter it is of the
first and most vital importance that its operation shall be effected under conditions
absolutely free from all extraneous influences; offering the least frictional retarda-
tion, and with a constant co-efficient of friction whatever be the pressure, or the
volume or the velocity of the flow. In the usual practice heretofore the subject
has been dealt with much as if it were a problem in hydrostatics alone, while as
a matter of fact it combines, or should combine a complete blending of principles
apparently well established both in hydrostatics and hydrodynamics. Thus to
illustrate I have found that, in the outcome of previous efforts in this direction
both of others and of myself, while practically perfect measurements and generally
satisfactory results were obtained at low velocity of flow, whether of small or great
volume, both the measurement, and the durability were unsatisfactory at a high
velocity and great volume of flow.

page_text: Therefore in searching for the cause and the remedy I have found that while the
valve-the vital part of a fluid meter of this class would be perfectly balanced as
to statical pressure, it would be still subjected to a portion of the force exerted by
the motion of the fluid. Therefore the sum of this force being directly as the
velocity of the fluid and the area of the obstruction presented, and as the valve
and its spindle necessarily lie within one or more of the sluices or chambers
traversed by the fluid, it will at once be apprehended that the power required to
operate the valve will also vary directly as the velocity of flow in consequence of
the friction developed in the bearings of the valve. Iovercome this diiculty by
neutralizing upon and by itself at the valve and its ports, each and every current
passing to the valve and from the valve which in any way can act to accelerate, or
to impede (by detrusion) the movement of the valve. Hence as the force of the
current is expended upon itself at and around all portions of the valve it will be
seen that its effect upon the movement of the valve is nil; and furthermore that.
the friction of the bearings of the valve will be a constant quantity namely; that
due to its weight. A construction whereby this result is obtained is illustrated in.
the drawings from Figs 11 to 20, the operation and arrangement of which is as
follows.
Entering at the ingress pipe 1. it will be seen that the fluid will be subjected to
an equal deflection and division at 2 and will pass both to the right and to the left
around the crown of the cylinder, through the ingress water way 3, until the two
currents thus formed, reach the valve casing 4. In said valve casing is formed a
longitudinal ingress sluice 5, which connects the two termini of the cylindrical
water way 3, and thus completes the first circuit to the induction port 6 (see
Figs 12 and 14) where the two currents meet upon each other and pass the port as
one current. Again dividing after passing the port it follows, both to the right and
to the left, as see arrows 8. 9 through the intermediate sluice 7 of the valve casing,
to the two connecting intermediate water ways 10. 11 of the upper cylinder. The
said waterways connect with corresponding waterways 12. 13 in the lower cylinder,
thus this circuit is completed to the lower compartment 14 formed by the piston 15
and diaphragm 16. The fluid beneath the piston and diaphragm will now act to
expel the fluid from the upper compartment 16a into and through the now open
eduction port 17 whence it will again find equal areas of exit through the egress
sluice 18 of the valve casing, dividing and passing both to the right and to the
left, connecting with and thereby completing the third and last circuit of the
cylindrical egress water way 19 of the cylinder. to, the egress pipe 20. Upon
the reversion of the valve to its alternate position assumed in Fig 14, the ingress
currents will again meet at the valve and valve ports, but will pass the now open
induction port 21, the egress current passing back through the intermediate sluices
as shown by arrows 22, 23 through the now open eduction port 24, and thence out
by equal deflections to the right and to the left as before Thus in the ingress
portion of the valve casing, the current is neutralized with respect to the valve by
continuous impact upon.itself. In the intermediate sluices the current, upon and
about the valve is neutralized by being. alternately forced upon itself, and forced
asunder; while in the egress sluice, the current is continuously forced asumder.
From the foregoing it will be apprehended that in whichever position the valve
may be, or whether seated or in transit, the ingress; the intermediate, and the
egress currents must necessarily draw away from or impinge upon each other at a..
right angle to the line of movement of the valve, and upon the longitudinal centre.
of the said valve, as the line 25 Fig 18 and can therefore have no effect either to
actuate the valve nor to retard its movement, the valve in fact being subjected to
two equal currents flowing in opposite directions It will be apparent that but
slight modifications would be necessary in this arrangement of water ways to adapt
the system to various styles of valves, and that the result will be the same whether
the passages be in the casing or in the valve or in both.
The manner described of forming water ways and sluices, permits them to be
made of. large area, and to be projected ou arcs of long radii, hence while the fluid

page_text: may have a high velocity through the pipe and ports, it will pass with reduced
speed but without impediment through the water ways and sluices. Furthermore
as no abrupt turns nor jogs are presented to the passing fluid it therefore suffers
but very slight loss of "head" from direct frictional resistance to its flow..
In constructing the water ways in the cylinder it might be completely accom-
plished by coring. This however would complicate, the process of molding and
casting, as the core could only be supported where it opens to the pipe, and to the
valve casing, besides which it would afterwards be difficult to remove the core.
I therefore prefer to cast or core these water ways with their lower portion partially
open, as from 26 to 27. Fig 18, coring out however where_connecting with the
valve casing as 28. 29. 30. as this leaves a solid surface, from which to machine the
taper, and against which to place the valve chamber. I then simply secure a plate
or cover as 31 over the open portions of the water ways, making a water tight.
joint, and the work is completed.
.
In this way, the molding and casting of the cylinder is of the simplest character
and the interior of the water ways may at any time be reached readily.
The screws 32 which secure the valve casing in position are placed in the solid
portions of the water ways as at 33. In the motor apparatus heretofore used to
operate the valve, a type of which has been herein before described, usually actuated
by a spring or weight, assuming the conditions of operation to be alike at slow and
fast flows the time required to throw the valve, will be of the same duration with
slow flows as with fast flows. The speed of the piston, however, at fast flows will
have been greatly increased; hence while the displacement may be exact at the
slow flows it will be increased-" over-run "-at fast flows. This is caused first by
the increased travel of the piston and second, by the increased velocity of the fluid
passing through the ports, the valve movement being constant while the flow and
velocity are variable, the reverse of positive valve actions, which may operate with
comparative satisfaction at fast flows but give most indifferent results, or are com-
pletely inoperative at slow flows, in consequence of the valve not being shifted
with sufficient rapidity or not being set completely over to its proper alternative
position. And when to this is added a variable condition of operation, the case
becomes more complex.
In view of the complete balance of the valve under every condition of operation,
as herein before described, I have been enabled-to fully overcome the difficulties just
cited and in the following manner.
Journaled at 36, on the same supporting arm 37 extending from the valve
casing as the bell crank 38 is what will be herein termed a multiplying lever 39
the extremity of which is engaged to the valve stem 40 by the slotted fork 41 and
pin 42. The toggle acting retaining springs 43 exert their thrust between the
thrust block 44 fast to the valve-stem to the bearings 45 of the spring carriage, to
the bell-crank, and thence through the 'slotted arin 46 of the bell crank to the
tooth or spur 47 of the multiplying lever. Thus the entire static energy of the
springs is utilized in "seating" the valve. In the position assumed in the figures,
the valve actuating apparatus is in position to be operated upon the up stroke of
the piston, during which stroke, the piston rod will engage the bell crank and
carry it upward. It will be observed that the slot. 48 of the arm of the bell crank,
is wider than the tooth, of the multiplying lever which it strides, and furthermore
.that any motion which may be imparted to the multiplying lever from the engage-.
ment of its tooth by the slotted arm will greatly augment the movement of said
multiplying lever at its point of engagement to the valve stem.
The relation of the slot 48 to the tooth 47 is such that upon the continued
movement of the bell crank, the sides of the slot will travel free of the tooth, until
just before or at the instant that the springs will have been brought to their dead
centre, when a side of the slot will impinge upon the tooth. It will now be seen
that the slightest additional movement of the piston rod will drive the multiplying
lever, and with it the valve stem and valve in an opposite direction to that of
the point 49a of the bell crank, and with much greater rapidity of. movement..

page_text: Meantime the springs are also acting upon the thrust block of the valve stem in the
same direction as the multiplying lever thereby adding their stored energy to that
of the piston.
.
T
+
To illustrate the action, assume the travel of the valve to equal say 2" and the
rate of movement of the multiplying lever to that of the piston as 5: 1. then
without taking into consideration, the effect of the springs the piston would only
have to travel 04" to place the valve in its alternative position (2″ ÷ 5 = '04″).
Although the chief function of the springs is to hold the valve in contact with its
seats in consequence of which they require to exert but slight force, they still assist
to throw the valve; thus giving out in useful effect whatever sum of energy will
have been stored within them by the piston in changing their direction of thrust
upon the valve. This arrangement of the springs and bell crank, while holding the
valve positively to its seat until the exact instant at which it should be thrown also,
at the same. instant, relieves the valve of all restraint, free to be acted upon by
the multiplying lever There is thus no shock nor appreciable strain upon the.
diaphragm, piston or connecting parts either in reversing the thrust of the retaining
springs or in actuating the valve.
The said multiplying lever and slotted arm of the bell crank are preferably
formed, as shown, to "straddle" their bearing, as in this way two slots and two teeth
are obtained which present a greater extent of bearing surface and centralize the
strain during its operation. It will be obvious however that like effects may be
had by a different arrangement of levers. The slot might be formed in the multi-
plying lever and the tooth on the arm of the bell crank, but the arrangement shown
is the better; as in this wise the strain is imparted to the multiplying lever more
nearly to the centre line connecting the bearings of the bell crank and said lever.
Were the construction reversed the strain would then be applied "off centre "at'
each alternative movement.
The springs 43 are formed somewhat like the letter S or a double inverted V.
The advantage of this form over the plain V spring of previous use is that its
tension, and promptness of action are alike in either direction of thrust.
As shown
in the diagram 12a the V spring in consequence of its hinge like movement from the
centre 49 will act more favourably when thrusting in the direction of the arrow 50
than in the opposite direction. In the S or double V spring 43 the same defect
exists but is neutralized upon.itself; the hinge action of the wing 51 being in the
direction of the arrow 52 while that of the wing 53 is in the opposite direction
arrow 54
The valve is constructed as shown in the enlarged figure 15. Against the shoulder
of the spindle is first placed an annulus of flexible packing 56. as rubber, leather etc,
next a thin "cupped" disc 57 formed from spring metal, the cupped edge of which 58
is slightly less in heighth than the thickness of the flexible packing which it
encompasses. Then a thin washer 59 is interposed between another disc and
packing similar to the first pair except that the cupped disc is reversed, thus placing
the two packings outside, as shown.
,,
The spindle bearing and shoulder 60 is then screwed into the tapped bearing 61
and the valve is complete. Each portion of the valve is thus "built up By
forming the metal disc in the mauner aforesaid it is comparatively rigid at its
periphery but is elastic and free to respond to any diaphragmatic action at its
centre, or as a ball and socket, in some phases of movement. The cupped or
unverted portion also serves to protect the edge of the packing from being worn
or collapsed by the impact of the currents through the valve casing.
The separation of the two discs by the washer 59 virtually provides a distinct
valve for each valve seat. Hence while one valve face may be continuously deflected
in one direction to adapt itself to some inaccuracy in its construction or to some.
interposed foreign obstruction, it will have no tendency to transmit the error to the
opposite face of the valve, which latter may be correct, or subject to deflection in
different degree, or different direction.

page_text: This form of metal disc is also of great utility when used as a metal valve with-
out packing either with an increased bearing surface as 62 Fig 16, or with the thin
edge of the metal itself as 63. Made in this manner simply the sharp edge of the.
disc requires to be ground to a surface the yield of its centre insuring proper fluid
tight contact on the valve seat.
In practice valves have been formed in the manner just described from sheet
metal but 005" in thickness.
Parenthetically it may be stated that the difference in pressure between the
ingress and egress sides of the valve is wholly dependent upon the friction
developed from all causes in the operation of the meter as a whole. As I have in
practice reduced the working pressure in certain instances to less than 02 of a
pound per square inch area it will be apprehended that there can be no possibility
of the thin elastic valve being collapsed upon itself from this or any analogous
cause.
To prevent the valve spindle from working apart where screwed together I slot
the outer end as at 64 and insert a pin 65 in the face plate bearing, said pin passing
freely through the said slot. The thrust block is also keyed or pinned to the front
bearing of the spindle, hence the entire structure when in operative position is
locked against the accidental disarrangement of its parts, which is likely to occur,
as is well known, in structures bound by screws and subject to the effect of
percussion.
To effect the greater economy of space it is necessary to pass the piston rod
through the valve casing as near as may be to the valve ports, and when the valve
casing is constructed as small as may be and serves its several functions this sets
the "crown or upper portion of the cylinder eccentric to the main body of the
cylinder, as indicated in full lines of Fig 13 and dotted outline of Fig 18. In this
manner less metal is required in the formation of the cylinder. The bearing for the
piston rod is formed through one of the partition walls of the valve casing and when
it is desired to use iron in the construction of said valve casing it becomes necessary
that the said piston bearing and the inner valve seats shall be of non corrosive
metal.
To obviate the cost of machining and fitting these parts I so construct the core
box which forins the system of cores for the valve casing as to receive and hold in
proper position, as a part of the core system, the tube 67 which forms the bearing
for the piston rod and the inner valve seats as 66 Figs 17 and 18. The core as a
whole is then placed in the mould and all the parts enumerated are cast in the
position they should occupy in the valve casing. Transverse slots as 68. Fig 17
may be cut in the periphery of the said valve seats to prevent them from turning
when being milled off.
But to ensure a water tight union of the valve seats to the iron partitions, and in
view of the fact that brass or bronze is superior to iron as an absorbent of heat and
that they will therefore become very hot, and will contract to a greater degree than
the iron when cold, I form the periphery of the said seats in any of the modes
shown as at 69. 70. 71 In this wise the superior contraction of the composition
will simply tend to hug the iron with the greatest intimacy. If forced as plain
annuli, they would shrink away from the iron and be loose and therefore useless for
the duty intended. With respect to the tube 67 as it is enclosed on all sides when
the valve casing is constructed of iron it only requires to be held from displacement
to which end it may be notched or grooved before inserting it in the mould, or
rivetted or otherwise secured if not sufficiently pinched by the iron. The piston is
formed from two stamped discs 74 whose norinal shape is shown in Fig 20. Each
is a duplicate of the other. The perimeters of the discs are flanged as at 74° and
thereby form a rounded bearing for the diaphragn and are stiffened against
deflection from a horizontal plane. To insert and confine the diaphragm it is
simply necessary to spring or "buckle" the centres of the discs inward towards
each other, and secure them by means of the hub and collar 75. Fashioned in this
manner the pinch upon the diaphragm is perfectly uniform regardless of how forcibly

page_text: the collar and hub may be brought together besides which the structure is made
exceedingly stiff from very light sheet metal and is simple to construct and to
assemble. The different forms of apparatus heretofore described have been shown
and set forth to illustrate different constructions embodying the main features of
this invention but it has been found that there are many advantages resulting from
modifying the construction in the manner illustrated in the remaining figures of the
drawing 21. to 27 which will now be described. The valve casing consists of the
body or cap piece 2. the bottom piece 1, and a removal chamber or sluice ring 4.
The cap or body 2 is constructed to form with the sluice ring a curved inlet
channel, a, communicating centrally with an inlet port c and a curved outlet
channel communicating centrally with an outlet port d and with vertical chan-
nels y z at the opposite sides with their upper ends between short partitions 7. 7.
The sluice ring 4 is constructed to form said channels a. b with the body portion
and has partitions 8. 8. constituting prolongations of the partitions -7. 7. and
between the inner ends of the partitions 8. 8 on opposite sides. fits a valve
casing 10. Below the sluice ring is a flexible diaphragm or piston 58 which is
connected with devices as fully described hereinafter to shift the valve to direct
the inflow to one side or the other of the piston and cause its rise and fall.
To avoid complicated core work and nice machine work within the cap piece 2
the main ingress and egress sluices a. b. are formed equally by the cylinder and
by the sluice ring 4 the closure of the sluices being effected by the contact of the
tapered faces 5. 6 at an angle This angle of contact is made as obtuse as possible
as shown, as this permits the use of thin pieces of packing, as rubber or gutta
percha between the surfaces of the sluice ring and cylinder, when by forcing the
sluice ring down snugly by means of the retaining screws 9 (Fig 24) the required
degree of closure is obtained without materially shifting the packing Thus any
inaccuracy in the metal surfaces will not materially affect the perfection of the
joint. In the same manner, a close joint between the valve case 10 and sluice
ring is secured. But in this instance the contiguous faces 11. 11a are simply
formed like a wedge, the angles of both being equal and even more obtuse than
those of the sluice ring and cylinder. A piece of packing cut to the shape of the
faces around the ports, is secured, or simply laid, in position, and the valve casing
is secured by the clamps 12 and screws 13. In this wise the joint can be readily.
made with but little fitting and the parts can be readily separated and be placed
accurately in position, and can be adjusted endwise or laterally, as will be
apprehended, across the ports, by varying the thickness of the packing on either
end. The valve 14 embodies the principles of a slide valve and piston valve, and
is so formed and arranged that in action it will be in perfect equilibrium under
constant or different static pressure and under direct and reactionary effects of
currents of either low or high velocity. The movements of the valve are effected
from those of the diaphragm 58 as will be hereinafter fully described. As shown
in the figures, the valve proper is simply a square or oblong frame of uniform
thickness, placed transversely across the valve casing and within the valve
chamber.
The operation and construction of the valve will be best understood by referring
to Figs 25 and 26. The valve is supported on a narrow longitudinal bearing 15,
at the lower portion of the valve chamber and is fitted to move freely within its
recess but sufficiently close to remain packed under any excess of pressure within
the ineter at any point. When the valve is in the position shown the ingress
current passes through the channel 24 and the port 19, into the chamber above the
diaphragm, the port 20 being closed by the forward end or section 28 of the valve,
port 21 being also closed by the back end or extension 25. The egress current
meantime is being forced through the intermediate sluice or channel 22 through
port 23, and thence out through sluice 24 as shown by the arrows. Both the outer
surfaces of the ends of the valve are exposed to the ingress pressure and both
the inner surfaces of the ends are exposed to the egress pressure. Whatever the

page_text: difference of pressure may be it will clearly be without effect upon the valve if the
latter is strong enough to bear it, that is there will be no effect from any difference
of pressure tending either to hold the valve or to shift it. It is also clear that as
the faces or edges of the valve which close the ports are under the equal effect of
the direct currents through the valve chamber the valve will operate without
friction or abrasion upon the portions of the channels between which it slides and
which it is intended to close. It has been found that when the difference of
pressure is but slight the valve may be fitted very loosely and the meter yet
operate with satisfactory results the film of fluid surrounding the valve being
maintained by the capillary attraction of the contiguous surfaces, the valve being
thus frictionless and waterpacked and without metal contact except on its bearing
at the bottom. It will furthermore be observed that the pressure on the inner
faces of the valve ends will also be in balance with respect to the direct and
reactionary effect due to the change of direction of the current from the inter-
mediate to the egress sluice or vice versa as its direct action and reaction is upon
equal areas of and borne by and between the parts of the valve itself. Upon the
outer faces of the valve ends, however, the reactionary effect due to the changed
direction of the ingress and egress currents is different.
In Fig 26 I have purposely omitted to illustrate one of the more important
features of my improved valve, the better to demonstrate the principle involved in
the portion to be now described.
Presuming that the valve chamber and valve are suspended and operated in a
vessel of infinite extent, the direct effect of the egress current would be entirely
expended upon the greater volume of fluid in which it was being forced, and would
therefore, retransmit its effect equally in all directions upon the mass of fluid;
hence its reaction upon the face 26. Fig 26 would be practically counteracted by
the indirect action through the fluid upon the face 25. In actual practice however
it is required that the mechanism of the instrument be placed in the minimum of
space, in consequence of which the effluent current will only partially expend the
force due to its velocity upon the greater volume of fluid in which it is projected,
and will pass through the said volume of fluid and expend the residual of its force
upon the confining walls of the meter. Consequently the direct action of the
current being only partially expended upon the fluid in which the valve is
suspended it can only return to the face 25 that portion of which will have been
taken up by the main body of fluid, while the reaction of that portion of the force
expended upon the rigid wall will be entirely returned to the face 26 of the valve.
To this extent, then the valve, and any valve under like conditions whether in
liquid or gas will be out of balance, and will require a varying expenditure of
power to shift its position, or in a ratio directly as the velocity of the current.
I obviate this difficulty by attaching to or forming as a part of the valve, the
counter pressure plates 29. 30. Figs 24 and 27. by which it will be seen that the
currents which pass the outer faces 25. 26 are caused to act and react within the
limits of the valve itself and hence regardless of their velocity will produce no.
effect upon the valve that in any way can assist or retard its movement. The
importance of thus eliminating each and all causes which can produce under any
condition of flow or pressure, singly or in combination, a deterrent or accelerative
effect upon the movement of the valve, is that I ain thereby enabled to perfectly
balance the valve against variations of pressure or flow, and to use a diaphragm of
very thin or elastic material, and yet obtain practically uniform displacement of
volume under all rates and conditions of flow and operation. The valve is also of
the most simple character, easily made and fitted. The counter pressure plates 29.30
need not necessarily be planed or ground, their surfaces being slightly beneath the
main body of the valve. A rock shaft 36 turns in bearings in standards 99. 99 and
carries a cross arm 35, to the ends of which are journaled the inner ends of rods 37,
the outer ends of the latter sliding in openings in brackets 93.. The valve is
actuated by toggle springs 31. 32, which are coiled on the rods 37, and upon being

page_text: drawn to either side slightly beyond their dead centre line. P. act through the
arms 33 carried by the rock shaft 36 directly upon at ooth or extension 34 of the
valve.
The action of the arms and springs are so timed relatively that the valve is put
into motion by the direct action of the piston slightly in advance of the movement
of the springs, thus the springs are not required to overcome the entire inertia of
the valve but take it at a speed at which the piston is moving. This also prevents
stoppage by obstruction of foreign matter.
When both springs are operative their thrust upon the journal is balanced, but
even in the event of one spring becoming partially or totally inoperative the other
would still act to properly operate the valve. The action of the springs arranged
in this way is also very prompt as soon as the dead centre is passed, as it will be
seen that each acts in the arc of a circle instead of at a tangent thereto as in other
devices. Upon the ends of each rod 37 is a connecting block 38, and also a sliding
and bearing block 39 between which is the spiral spring 32. This form of spring
is capable of being very thoroughly tested before use and it is durable and will
remain for a long time in an operative condition.
The compression of the springs and start of the valve is effected from the
diaphragm through the segment gear 40, fast to the shaft 36 which meshes with a
rack 41 sliding on the guide rods 42. From the rack projects a pin 43, and which
enters a slot in the piston rod 45 which is directly connected to the piston or
diaphragm 58 The advantage of this arrangement over an ordinary lever con-
nection is that the connection with the piston is direct, and that the actuating
springs may be elevated without correspondingly. increasing the piston rod and
height of the cylinder the connection with the rack being low down, while a lever
would require to be central and higher. A further advantage of this form of valve
and arrangement of actuating mechanism is the avoidance of "water hammer" or
pulsation in the pipe during the flow or at the reversal of the current through the
meter.
The combined area of the sluices or ports 46. 47, and also of 48. 49 slightly
exceeds the area of the ingress pipe.. In the illustration Figure 27, the thickness
of the valve is shown as a little less than half of the width of the ports past which.
it travels. It will be seen that immediately the valve is started both the ingress
and egress, currents are being cut off in like and equal extent and that when the
valve will have reached the position indicated by dotted outlines 50, the current
through the intermediate sluice and the cylinder of the meter will have been
correspondingly reduced in velocity. The valve continuing its transit opens the
ports previously closed, but the full velocity of the current will not be resumed,
until the valve will have reached its reverse position, indicated by dotted lines 51
in consequence of the valve closing a portion of the area required for passing a full
volume of fluid. Therefore although the described action of the valve is performed
with great rapidity its action is yet a cumulative one and a certain extent of time
is allowed in which to smoothly effect the expenditure of energy required to
reverse the current through the intermediate sluices, water ways and cylinder.
The movement of the valve is limited by the stops ✗, X, on the bearing piece 15
and the action of the arms 33 and springs is limited by the stop pin 44 as shown.
It will be apprehended thereby forming the valve sections to equal in thickness the
breadth of the sluices, that a complete stoppage of the flow would be effected at
each reversal of the valve, and that the meter would thus be mathematically exact
in the sum of its displacements. But this has not been found necessary in practice
and as the form described requires less movement to effect a full reversal and as it
reduces pulsations it is preferable.
This form also presents another advantage in that an obstruction which would
prevent the valve from fully reaching its proper position would not thereby render
the instrument totally inoperative, as the ports being open on the proper side, the
piston would operate at a less rate of speed until the valve was again shifted, and
the obstruction liberated.

page_text: It is evident that the counter pressure plates may be advantageously applied to
any or all of the various valve systems, and that the present forin of valve, might
be considerably modified without departing from the principle of its action, as it
might be wedge-shaped, circular, as a piston, vibrating or rotary valve. The
advantage of forming the valve casing in two portions is that each half may thus
be cast without coring to form the sluices, and as each face is a counterpart of the
others, they are made by a like means. The fitting of the valve is effected by
extension or reduction of the joint between the flanges at 52.
It will be observed that the disposition of the entire valve actuating apparatus
(as also tho register connections which are not shown in the figures) is above the
valve and the ports of the chamber; hence they are in
$1 dead water" and not
so liable to disarrangement as when other wise disposed. In constructing the
diaphragm 53 it is formed as a frustrum of a cone. By forming the pressure
cones 54 55 slightly curved inward in cross section, as shown at points 56, the
diaphragm is caused to roll upon them and operate with much greater perfection
than when caused to bear on a straight or oppositely curved section.
I also extend the cones above and over the piston, as at 57, thus completely
enveloping the diaphragm, so that any deposit of foreign matter will be sustained
upon the metal portion of the piston 58, or around the annular space 59 between
the cone and the cylinder. To secure the outer edge of the diaphragm, I form the
cones 54. 55 with parallel vertical flanges 60. 61 turned outwardly with sufficient
space between them to take and clamp the diaphragm snugly. An annular recess 62
is formed in the upper cylinder of such depth as to bring the outer surface, as 63
- flush with the face of the flange. The breadth of the flange of the lower cylinder
is such that it laps the flange of the cones. Therefore by inserting any suitable
plastic or yielding packing material between the flanges of the cylinders and wide
enough to lap. the flange of the cones, the diaphragm and cones will be securely
held in position without an injurious degree of compression and that this also
ensures a watertight joint between the two cylinders. It will be evident that
although different modes of constructing the meter have been set forth and
illustrated the same principles appertain to all.
Thus in each there is an outer casing consisting of two parts, capable of being
cast without coring, and of being bolted together, a detachable sluice ring forming
water channels with the casing, a transverse channeled portion, and a valve sliding
transversely to said portion, a flexible diapnragin, connected to operate the said
valve, and alternately lifted and depressed by water pressure alternately below and
above it, and that in each the water flows through the apparatus and registers its
flow with a minimum of friction and with accuracy whether the flow be great or
only drop by drop.
Having now particularly described and ascertained, the nature of the said
invention, and in what manner the same is to be performed, as communicated to
me from abroad by my foreign correspondent I declare that what I claim is
1. A detachable valve casing adapted to be placed within the outer casing of a
fluid meter to which casing is secured the operating parts of the meter substantially
as described.
2. The construction of the valve casing, spring valves and connections sub-
stantially as described.
3. The method and means of registering the flow of fluids through the meter as
set forth substantially as described.
4. The construction of the diaphragm together with the piston and the manner
of connecting the diaphragm to the piston and cylinders substantially as described.
5. The improved forms and construction of the cylinder or case, and the manner.
of uniting it, and the various parts of the meter substantially as described.
6. The improved system of water ways sluices and ports, whereby as perfect
equilibrium in the operation of the working parts of the meter is attained under
bydro-dynamic as under hydrostatic conditions substantially as described.

page_text: 7. The improved valve casing having water ways, sluices, and ports corresponding
to those of the case, and the manner of constructing such ways, sluices and ports
substantially as described.
8. The improved construction and arrangement of the valve seats, valve and
operating parts, whereby positive, rapid and accurate movements are obtained,
producing a correct register of the fluid flowing through the meter substantially as
described.
9. The casing formed in parts constructed to be cast without cores, the detachable
sluice ring, formning inlet and outlet channels with said casing, the transverse
channeled portion for transverse sliding valve, a flexible diaphragm, connected to
operate said valve under the pressure of water alternately on opposite faces all
substantially as set forth.
10. The valve operating mechanism provided with springs, arranged to throw
the parts positively to one side or the other after the dead centre is passed
substantially as set forth.
11. The arrangement of the flexible diaphragm below the valve chamber and the
valve operating appliances above the same and connections between said diaphragm
and the valve appliances substantially as described.
12. The improved modes of making and arranging the flexible diaphragm of a
fluid meter substantially as described.
13. The cap piece having upper and lower bearing faces at an obtuse angle, and
the sluice ring having corresponding bearing faces substantially as described.
14. The sluice ring having faces at an obtuse angle, and detachable valve casing.
fitting between said faces and with bearings corresponding thereto substantially as
described.
15. The valve sliding across a casing having a central, and side channels, and
consisting of a rectangular frame substantially as described.
10. The valve casing provided with central and side channels and with side
ports, in combination with a transverse frame valve and valve actuating piston
substantially as described.
17. The valve casing having central and side channels and lateral ports, in com-
bination with a frame valve, the ends of which are less in thickness than the width
of the side channels.for the purpose specified.
18. The combination with the valve, of plates connected thereto, arranged to
counterbalance the effect of water currents upon the ends of the valve, substantially
as described.
19. The combination of the casing, ports, channels, piston and valve, crossing
and controlling the ports, and carrying counter pressure plates for the purpose set
forth.
20. The valve casing in two parts, with an intermediate valve between said
parts, substantially as described.
21. The combination of the sliding valve rock shaft, its arm, rods connected to
said arm and sliding in bearings, and springs interposed between the bearings and
the arm, substantially as described.
22. The combination of the sliding valve, diaphragm, rock shaft carrying arms
arranged to make contact with said valve an arm on the rock shaft connected to
rods sliding in stationary bearings at the outer ends, springs around said rods, and
connections between the piston and rock shaft substantially as described.
23. The combination with the rock shaft and valve operating appliances of a
reciprocating diaphragm or piston and piston rod connected to the piston-and
geared or connected to rock the shaft as the piston rises and falls substantially as
described.
24. The combination of the outer casing with inlet and outlet ports and channels
valve casing, valve operating piston or diaphragm below the casing, and valve
actuating appliances, arranged above the casing and connected to bo operated by
the piston substantially as described.

page_text: 25. The diaphragm combined with cones arranged above and below the same
and curved inward, substantially as and for the purpose set forth.
26. The cones combined with the flexible diaphragm and provided with upturned
flanges adapted to a recess in the casing substantially as described.
27. The cones with inturned flanges at their inner edges and combined with the
flexible diaphragm as and for the purpose set forth.
Dated this faunth day of March 100%