Improvements in Water Meters.
Year: 1892

page_text: Date of Application, 24th May, 1892
Complete Specification Left, 19th Jan., 1893-Accepted, 25th Feb,
1893
PROVISIONAL SPECIFICATION.
Improvements in Water Meters.
I, JOHN THOMSON, of 190 Carrolton Avenue, Brooklyn, Kings County, in the
State of New York, United States of America, Engineer, do hereby declare the
nature of this invention to be as follows:-
This is an invention in water meters comprising a complete positive system
adapted both to the direct and to the proportionate measurement of fluids moving
under pressure.
To avoid repetition, the objects and advantages of the invention will be pointed
out as the description progresses, and to assist in clearing the description, the
distinguishing features of the device will be separately treated.
The means for accomplishing the results here sought, are capable of considerable
variation in detail, by those skilled in the art, without departing from its dominant
principles; 'hence, the mechanism by means of which I have chosen to illustrate
the invention, may be regarded as typical.
In the accompanying drawings,
Fig. 1, is a vertical, centre, longitudinal section of apparatus embodying my
invention.
Fig. 2, is a part plan view of the internal reducing gear train.
Fig. 3, is a plan view of the dial and pointers of the register.
Fig. 4, is a partial transverse section on the lines A and B of Fig. 1.
Fig. 5, is a partial vertical transverse section on the line C, of the external
valve casing 15, Fig. 1, and on the lines D, E, of the lower disc-casing 16, Fig. 7.
Fig. 6, is a top plan view, the upper disc-casing 17, being removed.
Fig. 7, is a top plan view, the upper disc-casing 17, diaphragm 18, disc 19, and
lower frustum 20, being removed.
Fig. 8, is a centre, horizontal sectional detail of the external valve-casing on the
line F, Fig.
1.
Fig. 9, is a detail plan view of the gasket.
Fig. 10, is a detail sectional view, enlarged, illustrating the manner of connecting
the flanges and of effecting the joint closure against pressure.
Fig. 11, is a bottom plan view, enlarged, of the controlling block 21, Fig. 1.
Fig. 12, is a part elevation and section of the disc, enlarged.
Fig. 13, is a vertical, centre, longitudinal section of apparatus similar in principle
to that of Fig. 1, but showing detail modifications.
The function of a proportional water meter is to inferentially measure, and to
indicate the same upon a recording register, a large volume by the actual measure-
ment of but an aliquot part thereof. To accomplish this it is necessary that the
ratio of the measured volume to that of the unmeasured volume shall be constant
under different rates of flow and variable conditions of friction. Hence, a primary
measuring device is a necessary component of such apparatus, and while it is true,
in the abstract, that almost any type of measuring mechanism might be employed,
yet, the fact is, that much depends upon the proper selection, design and construction
of this element of a proportional meter..
Therefore, upon the foregoing reasoning, I will take up the first general division
of the subject, namely: the measuring and recording mechanism. And as this is an
adaptation of the well known disc-action, the description thereof will be directed
only to the improvement therein.
The first improvement is in the manner of making the flange-joints, and of dis-
nosing the water_channels; whereby to avoid enclosing the disc-chamber casing

page_text: within separate pressure-resisting casings. Bearing in mind that the disc does not
roll upon the frustums but that a differential rubbing and rolling contact is
developed, the rubbing increasing with the increase of the angle from the horizontal,
it will be evident that the best arrangement to obtain a mean distribution of the
rubbing surfaces will be when the disc is flat and each of the frustums is inclined
equally from the horizontal. This requires that the disc chamber be divided on its
greatest diameter, which has heretofore involved the use of external pressure
resisting casings. I am enabled to avoid the use of such extraneous casings, and
yet retain the favorable conditions just pointed out, by forming a concentric
annular recess, as 22, Fig. 10, in either or both of the faces of the flanges 23, and
adapting to this recess a moulded gum rubber gasket 24, normally of less breadth
than the recess, but so much greater in thickness, that its cross-sectional area shall
be approximately equal to that of the cross-sectional area of the recess. The
recess is to be formed to leave an inner (25), and an outer (26), face bearing surface
which shall lie in the greatest horizontal plane of the disc chamber. A projection,
as 27, from the opposite flange is adapted to engage one or both of the vertical
sides of the recess, whereby to ensure the proper axial alignment of the two casings.
By this arrangement a property peculiar to gum rubber, (i.e. its practical incom-
pressibility when confined) is advantageously utilized; as when the flanges are
drawn together by the flange bolts, the rubber is simply caused to change its
original cross-sectional contour to conform to that of the free space between the
flanges. As the resistance to such distortion becomes greater and greater, with
the increase of friction produced by the pressure of the flange bolts, it is only
necessary to so gauge the mass of the rubber that it shall be properly within the
power of the flange bolts to draw the bearing surfaces of the Hanges together.
To facilitate this, the gasket may have a number of extra holes, as 28, between the
bolts, permitting the rubber to displace internally as well as externally. Thus, an
absolutely tight joint is readily obtainable to resist high internal pressure, while
it is yet insured that the metallic faces of the flanges shall be brought to an
unalterably fixed gauge position; the internal spherical contour of the disc chamber
being unbroken, except only by the line of contact at the metal surfaces of the
flanges.
The second improvement relates to the manner of conveying the flow to the disc
chamber H, whereby to economize in space and material; which features are more
or less contingent upon the manner of jointing the casings already set forth.
Were
the measuring mechanism to be used separately, as a direct meter of minimum
capacity, then the pipe connections would preferably be applied to the lower casing,
each diametrically opposite to the other, as indicated by the dotted outlines 30, 31;
the water from the inlet pipe being conducted by a cored channel to the chamber I.
But as here shown, the inlet to this chamber is through the opening 32, whence
the water passes cross-wise in horizontal section, thence passing outwardly and
upwardly into the vertical space 33, formed by the off-set or housing 34, of the
disc chamber casings, as see Figs. 5, 6 and 7. This vertical space is in fact the
supply or inlet port of the disc chamber; the entire inner portion of this space
merging therein to the extent of the height of the said chamber. The vertical
space where it merges into the chamber 1, is carefully curved, as 35, so that the
centrifugal effect imparted to the moving volume shall tend outwardly against the
exterior wall of the vertical space and beyond the sweep of the disc throughout
its oscillation. Obviously, considerable of the energy of the rapidly flowing water
when it passes into the curved section, will be expended in friction upon the outside
wall, then by impact upon the abutment or "dead-end," 36, and thence, reacting
against the exterior wall, as indicated by the arrows a, will thus be forced into the
disc chamber at approximately a right line, or in the plane of the disc chamber,
thereby producing the minimum of disturbance upon the ball and socket bearing
of the disc. In other words, the original direction of. flow through the chamber I,
is completely reversed, and its velocity reduced at the instant of the delivery into
the disc-chamber to an extent nearly, if not quite, equal to that due to the area of

page_text: the disc-chamber. The discharge from the disc chamber is directly to another
vertical space 40, analogous to that just described whose receiving capacity is
approximately equal to the delivering capacity of the disc chamber. The advantage
of this design and construction is that destructive velocity against the disc is
avoided with no greater increase of space or material than would be involved if the
delivery of the water from the inlet pipe was directly against the disc at maximum
velocity, whence much of its energy would be expended upon the ball and socket
bearing with unsatisfactory results in practice, as has frequently been proven.
The third improvement relates to the construction of the casing to form the
disc chamber, and consists in producing the spherical contour 42, of the disc
chamber in the main casings, terminating in shallow cylindrical bearings 43, having
stops or shoulders 44. The frustums 20, 45, provided with bearing sockets for the
ball, are formed separately, the peripheries and faces of which, opposite to the
conical surfaces, are adapted to the aforesaid cylindrical bearings to which they are
placed from the interior of the casings; their proper relative positions being, thus
established both vertically and horizontally. The diaphragm 18, is secured in
position by inserting its upper and lower edges into slots formed in the faces of the
frustums. The lower frustum 20, is secured to the bottom of the casing, as by the
screw 46, the attachment of which completes the closure of the chamber I, and
also secures the frustum in place against any difference of pressure between the
said chamber and the disc-chamber.
The fourth improvement refers to the control of the disc. In Fig. 6, the disc 19,
for convenience and clearness of illustration, is shown tilted up to lie in the hori-
zontal plane of the disc chamber. The complete control of the disc involves means
for taking its thrust due to the flow around the disc chamber, arrows b, and also
means for preventing it from leaving the frustums. The axial thrust of the disc,
that due to the flow, is ordinarily resisted by the diaphragm alone, but for this
purpose I provide an additional abutment 48, projecting slightly into the chamber,
disposed diametrically opposite to the diaphragm, and which is engaged by the
shallow slot 49, of the disc. In this wise, the receiving and discharging edges: 50,
of the disc, where they embrace the diaphragm, may be left out of contact there-
with, thus providing free water passages thereat. But I prefer to provide the
diaphragm with a rounded face bearing, as 51, so that the disc may be controlled
by either or both of the bearings. In the instance of both bearings being employed,
there is less tendency to cramp the disc when driven at high rates of speed. The
proper contact of the disc upon the frustums is maintained by the spherical edge
of the circular bearing block 21, Fig. 1, impinging upon the disc spindle 52; which
result is obtained by mounting the block upon the cylindrical journal bearing 53,
formed upon the lower surface of the fixed gear 54. The block, not being positively
connected to the disc-spindle, is free to rotate, or to slightly rise or fall upon its
bearing, or to remain stationary. The gear train is driven by the arm 55, fast, to
the primary pinion 56, of the reducing train. The block being thus free to move
rotatively and also to reciprocate, will descend until arrested by the disc-spindle, when
it may either revolve upon its cylindrical bearing due to its contact with the spindle,
or it may remain stationary, the spindle rotating around its spherical edge. Now,
should a foreign obstruction pass between the disc and one of the frustums, the
block, in consequence of the angular thrust of the spindle transmitted to the
cylindrical bearing, would be driven upward and the disc would thus be instantly
relieved; the block, however, tending to reset the disc upon the passage of the
obstruction. In this wise, too, the block automatically adapts its normal position
to the spindle, requiring no nicety of vertical adjustment in the several parts.
The fifth improvement is in the reducing gear train, which improvement consists
in forming hubs 57, upon the intermediate pinion 58; in adapting these hubs to the
grooves or recesses 59, formed in the fixed and free differential gears 54, 60, in
attaching the free gear directly to the stuffing box spindle 61, and in securing the
fixed gear, as by means of the screws 62, directly to a bearing 63, formed in the
upper disc casing. In this wise no additional mounting whatever is required,

page_text: the fixed gear serving to provide the bearing for the controlling block, and also for
the pivot of the primary pinion. While I am aware that the principles employed
in this reducing train-that is, a combination of the epicyclic and differential-are
well known, yet the manner of applying them to the present purpose and of
mounting the free pinion in the annular grooves so that the thrust is resisted by
approximately rolling contact between the hubs and the walls of the grooves, are
novel, yielding the important advantages of low cost, great durability, compactness,
and reducing the frictional resistance between the disc and the stuffing box to a
minimum.
The sixth improvement consists in the design of the ball and disc whereby they
may be made of hard rubber moulded together as one part with sufficient accuracy
not to require additional finishing. Attempts in this direction heretofore have
been unsuccessful, in that the greater thickness or mass of the ball as compared
to the distribution of material in the disc, has resulted in unequal and variable
shrinkages. This I overcome by the simple expedient of providing the die with an
inwardly projecting metal core, central to the ball, vertical to the plane of the
disc, so that the heat, during the vulcanizing process, is conducted to the ball both
from the exterior and from the interior thereof, and owing to the uniformity of
heat-conduction thus effected, this important member of this meter may not only
be made very accurately, but of what is even of greater importance, with the
utmost uniformity. By not passing the metal core entirely through the ball, but
projecting it inwardly from either side, the ball is thus produced with two cylin-
drical openings 64, leaving a partition 65, in its centre, which provides a convenient
and rigid base for the attachment of the disc spindle, as shown.
The seventh improvement is in forming shallow grooves 66, in the ball and also
in the periphery of the disc, the object of which is to provide clearance-spaces
wherein particles of sand or other foreign material liable to be forced : between
the bearing surfaces, may enter these spaces and eventually work their way out,
instead of being retained to cut and wear the bearings.
The eighth improvement relates to the dial and pointers of the register.
The dial is shown as having a circular face, upon which are arranged a number
of circular graduates, and to be used with each graduate is a pointer, which is so
constructed and arranged that it shall not in any way cover the numerals or
indices upon the face of the dial, the pointer not reaching out to the numerals,
but revolving within a circle bounded thereby; thus as the pointer rotates, all of
the numerals or indices will be exposed to view. In order that the dial may be
accurately read, I construct the pointer with one of its edges 67, straight and
radiating from the centre of its pivot towards the numerals, while the other
edge 68, of the pointer is curved, being shown as curving from its outer extremity
to the hub. The intersection of the straight edge or radial projection with the
hub is sharply nicked, as at 69, to more clearly define the straight edge.
f.
By this construction, while the figures or other indices on the dial are at all
times fully exposed to view, the pointers being of less radius than the indices and
not reaching out to them, the sharply defined straight edge furnishes a guide to
the eye for accurately reading the numerals; the exact coincidence of the pointer
with any particular graduation, being much more certainly defined than by the
ordinary form heretofore used; as it will be seen that this requires that three
points be brought into alignment, two of which are moving at unequal velocities.
In order to further aid in accurate reading, I arrange the graduating lines so
that they will project inwardly to a considerable extent towards the centre and
thus form on the face of the dial, a series of recesses apparently having an open
inner side towards the pointer, while the other sides are composed of a segment
of the circumference of the enclosing or boundary circle and the two inwardly.
projecting graduations. I then arrange in these recesses the numerals or other
indices which correspond to the value of each space which should be given to the
pointer during its travel through any given recess, or from one graduation to the
other.'

page_text: The second general division of the subject relates to the method and means for
controlling the proportional flow and the relation thereof to the measuring
mechanism. That portion of the apparatus now to be described is positively
operated by the differences of pressure between a plurality of chambers, one of
which (hereinafter termed the controlling chamber) receives the discharge from
the measuring mechanism. The result desired to be accomplished is to cause a
positive increase of resistance to the entire flow to follow any decrease of pressure
in the controlling chamber, and vice versa, upon an increase of pressure therein.
Then furthermore, means and conditions are provided whereby the proper operation
of the device as a whole shall not be liable to disturbance in its proper function by
changes in the velocity of flow.
The entire proportional valve-device is contained in the main external casing 15.
The positive pressure piston 71, operates in the cylinder 72, of the valve-casing 14;
chamber of which is placed in direct communication with the main inlet
chamber K, by the opening 73. The valve 74, which is an open ring supported
on its hub by arms 75, operates in a cylinder 76, which opens its full capacity
directly to the main outlet chamber M. The negative pressure piston 77, operates
in the intermediate cylinder 78, the forward end closure of which is effected by
fixed partition 79, through a bearing in which the valve spindle 80, freely operates.
The intermediate chamber N, of the valve-casing is suitably connected, as by the
opening 81, to the separate controlling pressure chamber P, while the negative
chamber R, is connected to the main outlet chamber by a channel as 82, through
the valve spindle and the lateral openings 83, connected therewith. The object of
supporting the valve by the arms 75, is that the water may be free to displace
from one side to the other of the valve. The positive pressure piston 71, is in fact
a plunger extending outwardly from the negative pressure piston 77; the area of
the positive piston being less than that of the negative, and these pistons taken
together might properly be termed a differential piston. The object of the
channels 82 and 83, is to permit the free displacement of water to and fro between
chambers R and M. The piston, the valve, and the spindle are all connected
together as shewn, to act as one part.
The delivery from the main inlet chamber K, to the main outlet chamber M, is
entirely through a series of ports, as 84, 85, radially disposed and preferably
formed in a single transverse plane, as line C, of the outlet cylinder 76, of the
valve casing. In the drawing two of these ports 84, provide direct communication
between the main inlet and the outlet chambers, (arrows d) while the remaining
port 85, provides communication between the controlling chamber and the main
outlet chamber only, (arrow e). The controlling chamber is connected by the
opening 86, to the vertical outlet space 40, of the measuring mechanism, while the
receiving chamber 1, of the measuring mechanism is connected by the opening 32,
directly to the main inlet chamber K. A's the areas of the several ports are
equal each to the other the presumptive ratio, therefore, of the measured' to the
entire volume is as 3: 1.
From the foregoing it will now be seen that all of the ports will be controlled by
the single valve 74 that two-thirds of the whole volume will pass directly from
the outside to the inside of the valve casing, while the final third portion will first
pass through the opening 32, then through the receiving and disc chambers of the
measuring mechanism, next by the channel 40, and through the opening 86, to the
controlling chamber P, then through the port 85, to the outlet cylinder of the valve
casing, and thence will pass on with the quantities received through ports 84, as
an integral part of the entire volume.
"
I will give numerical values to the areas of the positive and negative pistons, as
in this wise a more ready comprehension is derived of the operation of the device.
Thus, assume the area of the positive piston 71, to be 1·00 square inch and the
effective area of the negative piston 77 to be 2.00 square inches; whence the
difference between the piston faces is, 200-100 = 1 square inch, the excess of
area of the negative piston over that of the positive.
1

page_text: The operation is as follows:-Assume the valve in the position indicated by the
full lines of Fig. 1, in which the ports are partially closed, and that an increased
draft is made causing an increased difference or pressure between the main inlet
and outlet chambers K and M. Then suppose the difference of pressure thus
produced between these chambers to equal 1 pound to each square inch; whence
1 pound will be exerted upon the positive piston, tending to force the valve forward.
Meantime pressure will also have been transmitted through the measuring
mechanism, to the controlling chamber, and thence through the opening 81, to the
intermediate chamber N, of the valve casing. The extent of the pressure which
will reach the controlling chamber, to each unit of surface, will be equal to that
of the main inlet chamber less the power absorbed in passing through the channels
and in operating the measuring device.
-
0.25 =
Assume this absorption of pressure in passing from chambers K; to P, as equal
to 0.25 pound to each square inch; then the effective pressure, to each unit of
surface, transmitted into the controlling chamber will be 1-0
0.75 pound,
whence, the sum of the power exerted upon the negative piston to force the valve
backward will be, 2 x 0.75 = 1.50 pounds. Consequently, as the sum of the
power exerted upon the negative piston is greater by 0.5 pound than that exerted
upon the positive piston, the valve will in fact be moved backward, causing it to
open the ports; which action will continue until the opposing forces are balanced,
that is to say, when the sum of the pressure upon the faces of the pistons (not the
pressure upon each unit of surface) will be equal to the other. During such action,
water will flow from chambers P to N, and be displaced from R to M.
Again, if after such a condition of equilibrium has been established, there shall
from any cause be an increase of resistance to the flow through the measuring
mechanism, this will decrease the pressure both in the controlling chamber and
also in the intermediate chamber. The further effect of such obstruction, in con-
sequence of decreasing the delivery into the controlling chamber, will be to
increase the pressure in the main inlet chamber. Therefore, as the sum of the
power upon the negative piston is decreased, while that upon the positive piston is
increased, the valve will be driven forward, causing it to throttle all of the ports
which action will be continued until another position of equilibrium will have been
established, as before, between the opposing forces.
During any movement of the valve the fluid which enters or is displaced from
chamber R, passes, as already stated, through the channel in the spindle to or from
the main outlet chamber. Hence, the said chamber R, is negative to chamber N ;
the pressure in the said chamber R, being practically identical with that in the
main outlet chamber. In fact, at rapid rates of flow, the pressure in chamber R,
may be less than that of the main outlet chamber, owing to induction due to the
flow past the end of the spindle; which is projected well forward, as shewn,
towards the main outlet chamber to prevent any re-active effect from reaching the
negative chamber R.
From the foregoing it will be seen that the position of the valve with respect
to the ports is a resultant of the following conditions, namely; the pressure in the
main inlet chamber K, the pressure in the main outlet chamber M, the pressure
in the controlling chamber P, and the pressures in the several chambers of the
valve casing.
Furthermore, that any fluctuations of pressure in the controlling chamber alone
will result in a co-action of pressure in each and all of the chambers; the
immediate consequence of such co-action being to cause the valve to throttle, to a
greater or lesser degree, all of the ports, in any instance when the pressure in the
controlling, chamber decreases; and to cause the valve to open all of the ports, to
a greater or lesser degree, when the pressure therein increases. In other words,
the power absorbed in overcoming the hydraulic and mechanical friction necessary
to the operation of the measuring mechanism creates a difference of pressure, which
acts as a balance or governor to determine the relative position of the valve with
respect to the ports.

page_text: In the drawings, have shewn a spring 87, which may be employed to co-act
with the pressure upon the positive piston. It has also another function, which
is, in the event of suddenly stopping a rapid flow of water, this might leave the
ports open, but with the spring as an auxiliary this could not occur, as the spring
would force the differential pistons and valves forward and close the ports. The
employment of the spring, or its equivalent, (as a weight) in no wise affects the
described operation of the device, as it but increases the intensity or difference of
pressure between the main inlet and controlling chambers and that of the main
outlet chamber.
Means are also provided for still further compensating or balancing the hydraulic
conditions, consisting of the circular rib 88, formed transversely in the main casing,
leaving an annular space or spaces 89, bounded by the inner edge of the rib and
the valve casing. The function of these ribs is to restrict or throttle the flow from
that portion of the main inlet chamber, which is connected to the measuring
mechanism, and the forward portion which supplies the ports 84, as see arrow i.
By a proper relative proportionment of the areas of the spaces 89, it will be
evident that the water may be delivered under practically identical conditions as
to pressure where leading to the ports 84, and also to port 85. And obviously,
the more nearly this can be accomplished without mechanical intervention, the
more accurate will be the action of such devices as may be employed.
I prefer to situate the valve-casing in the axis of the main casing, as the
most compact construction is thus obtainable, the diameter of the main casing
requiring to be but a trifle greater than that of the supply pipe with little or
no complication in casting the parts. In this wise, too, the machining operations
are exceedingly simple, consisting only in boring a cylindrical bearing length-
wise of the main casing and adapting the valve casing thereto.
The function of the screw 90, is to prevent the valve-casing from being forced
out of its bearings by pressure.
I prefer to form the ports circular, as shewn, by simply drilling a series of
holes through the valve casing, whose number shall preferably correspond to
the desired proportional ratio, as in this manner, the ratio as between a number
of meters may be obtained with the utmost uniformity. Then, too the several
edges will be caused to open exactly simultaneously; which, while subtending
a constant ratio for every increment of novement of the valve, yet affords but
a small total area at low rates of flow; rapidly but constantly, increasing the area
with any increase in the rate of flow.
The attachment of the measuring mechanism to the main valve casing is con-
veniently accomplished by means of the screws 91, applied from the interior of the
lower disc chamber casing. There are, however, no great difficulties in the way of
casting the lower disc chamber casing and the main valve casing together as one
part. But there are some advantages in the present arrangement in the more ready
adaptation of these parts to machine processes.
The controlling advantages derived from this construction and disposal, yet
remain to be pointed out, and may be thus summarized. By thus ejecting the
volume from the main inlet chamber and from the controlling chamber in a series
of jets which converge in the accurately finished cylinder of the valve casing, one
jet impinging against another, all finally reacting and passing on through the pipe
as one volume, as see arrows d, e, a perfectly balanced condition of flow, is obtained
and that too, at the precise place and instant where the proportional control is
effected. This is a most important feature, as I have found that many heretofore
apparently inexplicable fluctuations in the performance of proportional meters were
caused by the erratic effects produced by currents of different velocities. This I
may illustrate in the instance of two jets discharged under equal pressure past a
valve from inside to outside of a casting; one jet impinging against a fixed con-
tiguous wall, the other jet ejected in the general direction of flow. In the former
instance a considerable portion of the kinetic energy would be absorbed by shock
and eddies, while in the latter instance practically all of the energy would be

page_text: •
merged into the common velocity of the main stream, Obviously such effects will
increase, more or less constantly, with the increase in the rate of delivery and as
the velocity through the controlling passages of proportional meters must be
relatively high to accomplish one of the special objects sought (compactness), such
erratic disturbances make it more difficult to maintain an exact proportional
measurement by means of automatic apparatus operated by differences of dynamic
pressures. In other words were this not provided for, there would be a variable
condition with which mechanical appliances could hardly be expected to success-
fully cope, because such effects establish different intensities of pressure in the
same chamber. But by the present simple expedient of causing the entire volume
to pass from the outside to the inside of the valve casing, each particle impinging
upon another and all subject to precisely the same deflections, the dynamic condition
thus established is nearly, if not quite, theoretically perfect and will bear a constant
relation under all rates of delivery. In disposing all of the controlling ports, both
of the measured and of the unmeasured quantities in a single plane of the valve
casing, all the ports being governed by the single valve, difficulties of adjustment
for "lap" and "lead" are thereby avoided. Then, too, the direction of the flow is
toward the centre away from the casing, and away from the valve; the tendency
being to wash the valve and carry sand or other foreign substances away therefrom.
Furthermore, this feature otherwise very greatly reduces the liability of the pistons
to become clogged or worn, in that there is no flow either to or from any of the
valve casing chambers, except only during a shift of the valve, as it is to be
particularly observed that the positive piston both receives from and displaces back
to the main inlet chamber, arrow ; that the negative piston both receives from
and displaces back to the controlling-chamber, arrow r, while the actual flow is
entirely through the outlet cylinder 76. Thus, if the draft is at a constant rate
and an ordinarily constant frictional condition of the measuring mechanism prevails,
then the valve would stand as if fixed, and the pressure in the valve casing
chambers J, R and N, would be static. Moreover, the entire flow will be stopped
should the measuring mechanism fail to operate and by such failure prevent the
measured proportional part from reaching the controlling chamber, as in such
event, pressure would only be exerted upon the positive piston; which would drive
the valve forcibly forward, closing off all of the ports. Neither can the meter be
operated backward, as should the outlet be applied to the inlet end of a pipe, the
pressure would be transmitted to the chamber R, through the channel 82, which
pressure would maintain the valve in position and the ports would be kept closed.
The modifications in detail shewn in Fig. 13, are presented to indicate the
readiness with which the device may be changed in some particulars, without
departing from the spirit and function thereof, wherefor I do not limit myself to
the precise terms and details submitted, to illustrate my invention. It is not deemed
necessary to make any description of these modifications, as the several details
thereof, corresponding to the preceding figures of the drawing, are carefully indicated
by the same reference letters and numerals.
The commercial advantages of this system are of the greatest importance, as its
manufacture involves the construction of but one size of measuring mechanism;
which being adaptable to any size of valve casing simply involves a plurality of
valves and valve-cylinders, suitably standardized as to the ratio of their ports,
whereby to meet the requirements of actual practice. Thus in the drawing, the
measuring mechanism, as Z, may be taken as representative of both of the minimum
and of the direct positive portion of the system; or Z and Y, the latter denoting
the full lines of the valve and valve casing, together comprising the next regular
commercial size, embodying the combined system of direct positive and positive
proportional while, again Z and the dotted outline W, indicate a still larger
capacity.
· Dated this 24th day of May 1892.
PHILIP M. JUSTICE, Fel. Chart. Inst. P.A.,.
55 & 56, Chancery Lane, London, Applicant's Agent.

page_text: developed, the rubbing increasing with the increase of the angle from the horizontal,
it will be evident that the best arrangement to obtain a mean distribution of the
rubbing surfaces will be when the disc is flat and each of the frustums is inclined
equally from the horizontal. This requires that the disc-chamber be divided on
its greatest diameter, which has heretofore involved the use of external pressure
resisting casings. I am enabled to avoid the use of such extraneous casings, and
yet retain the favorable conditions just pointed out, by forming a concentric
annular recess, as 22, Fig. 10, in either or both of the faces of the flanges 23, and
adapting to this recess a moulded gum rubber gasket 24, normally of less breadth
than the recess, but so much greater in thickness, that its cross-sectional area shall
be approximately equal to that of the cross-sectional area of the recess. The
recess is to be formed to leave an inner (25,) and an outer (26), face bearing
surface which shall lie in the greatest horizontal plane of the disc chamber. A
projection, as 27, from the opposite flange is adapted to engage one or both of the
vertical sides of the recess, whereby to ensure the proper axial alignment of the
two casings. By this arrangement a property peculiar to gum rubber, (i.e. its
practical incompressibility when confined) is advantageously utilized; as when the
flanges are drawn together by the flange bolts, the rubber is simply caused to
change its original cross-sectional contour to conform to that of the free space
between the flanges. As the resistance to such distortion becomes greater and
greater, with the increase of friction produced by the pressure of the flange bolts,
it is only necessary to so gauge the mass of the rubber that it shall be properly
within the power of the flange bolts to draw the bearing surfaces of the flanges
together. To facilitate this, the gasket may have a number of extra holes, as 28,
between the bolts, permitting the rubber to displace internally as well as externally.
Thus, an absolutely tight joint is readily obtainable to resist high internal pressure,
while it is yet insured that the metallic faces of the flanges shall be brought to an
unalterably fixed gauge position; the internal spherical contour of the disc chamber
being unbroken, except only by the line of contact at the metal surfaces of the
flanges.
The second improvement relates to the manner of conveying the flow to the disc
chamber H, whereby to economize in space and material; which features are more
or less contingent upon
the manner of joining the casings already set forth. Were
the measuring mechanism to be used separately, as a direct meter of minimum
capacity, then the pipe connections would preferably be applied to the lower casing,
each diametrically opposite to the other, as indicated by the dotted outlines 30, 31;
the water from the inlet pipe being conducted by a cored channel to the chamber I.
But as here shown, the inlet to this chamber is through the opening 32, whence the
water passes cross-wise in horizontal section, thence passing outwardly and upwardly
into the vertical space 33, formed by the off-set or housing 34, of the disc chamber
casings, as see Figs. 5, 6 and 7. This vertical space is in fact the supply or inlet
port of the disc chamber; the entire inner portion of this space merging therein to
the extent of the height of the said chamber. The vertical space where it merges
into the chamber I, is carefully curved, as 35, so that the centrifugal effect imparted
to the moving volume shall tend outwardly against the exterior wall of the vertical
space and beyond the sweep of the disc throughout its oscillation. Obviously,
considerable of the energy of the rapidly flowing water when it passes into the
curved section, will be expended in friction upon the outside wall, then by impact
upon the abutment or "dead-end," 36, and thence, re-acting against the exterior
wall, as indicated by the arrows a, will thus be forced into the disc chamber at
approximately a right line, or in the plane of the disc chamber, thereby producing
the minimum of disturbance upon the ball and socket bearing of the disc. In other
words, the original direction of flow through the chamber 1, is completely reversed,
and its velocity reduced at the instant of the delivery into the disc-chamber to an
extent nearly, if not quite, equal to that due to the area of the disc-chamber. The
discharge from the disc-chamber is directly to another vertical space 40, analogous
to that just described whose receiving capacity is approximately equal to the

page_text: delivering capacity of the disc chamber. The advantage of this design and con-
struction is that destructive velocity against the disc is avoided with no greater
increase of space or material than would be involved if the delivery of the water
from the inlet pipe was directly against the disc at maximum velocity, whence much
of its energy would be expended upon the ball and socket bearing with unsatisfactory
results in practice, as has frequently been proven.
The third improvement relates to the construction of the casing to form the disc
chamber, and consists in producing the spherical contour 42, of the disc chamber in
the main casings, terminating in shallow cylindrical bearings 43, having stops or
shoulders 44. The frustums 20, 45, provided with bearing sockets for the ball, are
formed separately, the peripheries and faces of which, opposite to the conical
surfaces, are adapted to the aforesaid cylindrical bearings to which they are placed
from the interior of the casings; their proper relative positions being thus
established both vertically and horizontally. The diaphragm 18, is secured in
position by inserting its upper and lower edges into slots formed in the faces of the
frustums. The lower frustum 20, is secured to the bottom of the casing, as by the
screw 46, the attachment of which completes the closure of the chamber I, and also
secures the frustum in place against any difference of pressure between the said
chamber and the disc chamber.
The fourth improvement refers to the control of the disc. In Fig. 6, the disc 19,
for convenience and clearness of illustration, is shown tilted up to lie in the hori
zontal plane of the disc-chamber. The complete control of the disc involves means
for taking its thrust due to the flow around the disc chamber, arrows b, and also
means for preventing it from leaving the frustums. The axial thrust of the disc,
that due to the flow, is ordinarily resisted by the diaphragm alone, but for this
purpose I provide an additional abutment 48, projecting slightly into the chamber,
disposed diametrically opposite to the diaphragm, and which is engaged by the
shallow slot 49, of the disc. In this wise, the receiving and discharging edges 50,
of the disc, where they embrace the diaphragm, may be left out of contact there-
with, thus providing free water passages thereat. But I prefer to provide the
diaphragm with a rounded face bearing, as 51, so that the disc may be controlled
by either or both of the bearings. In the instance of both bearings being employed,
there is less tendency to cramp the disc when driven at high rates of speed. The
proper contact of the disc upon the frustums is maintained by the spherical edge
of the circular bearing-block 21, Fig. 1, impinging upon the disc spindle 52, which
result is obtained by mounting the block upon the cylindrical journal bearing 53,
formed upon the lower surface of the fixed gear 54. The block, not being positively
connected to the disc-spindle, is free to rotate, or to slightly rise or fall upon its
bearing, or to remain stationary. The gear train is driven by the arm 55, fast to
the primary pinion 56, of the reducing train. The block being thus free to move
rotatively and also to reciprocate, will descend until arrested by the disc-spindle,
when it may either revolve upon its cylindrical bearing due to its contact with the
spindle, or it may remain stationary, the spindle rotating around its spherical edge.
Now, should a foreigu obstruction pass between the disc and one of the frustums,
the block, in consequence of the angular thrust of the spindle transmitted to the
cylindrical bearing, would be driven upward and the disc would thus be instantly
relieved the block, however, tending to reset the disc upon the passage of the
obstruction. In this wise, too, the block automatically adapts its normal position
to the spindle, requiring no nicety of vertical adjustment in the several parts.
The fifth improvement is in the reducing gear train, which improvement consists
in forming hubs 57, upon the intermediate pinion 58, in adapting these hubs to the
grooves or recesses 59, formed in the fixed and free differential, gears 54, 60, in
attaching the free gear directly to the stuffing box spindle 61, and in securing the
fixed gear, as by means of the screws 62, directly to a bearing 63, formed in the
upper disc casing. In this wise no additional mounting whatever is required,
the fixed gear serving to provide the bearing for the controlling block, and also for
the pivot of the primary pinion. While I am aware that the principles employed

page_text: in this reducing train—that is, a combination of the epicyclic and differential-are
well known, yet the manner of applying them to the present purpose and of
mounting the free pinion in the annular grooves so that the thrust is resisted by
approximately rolling contact between the hubs and the walls of the grooves, are
novel, yielding the important advantages of low cost, great durability, compactness,
and reducing the frictional resistance between the disc and the stuffing box to a
minimum.
The sixth improvement. consists in the design of the ball and disc whereby they
may be made of hard rubber moulded together as one part with sufficient accuracy
not to require additional finishing. Attempts in this direction heretofore have been
unsuccessful, in that the greater thickness or mass of the ball as compared to the
distribution of material in the disc, has resulted in unequal and variable shrinkages.
This I overcome by the simple expedient of providing the die with an inwardly
projecting metal core, central to the ball, vertical to the plane of the disc, so that
the heat, during the vulcanizing process, is conducted to the ball both from the
exterior and from the interior thereof, and owing to the uniformity of beat-
conduction thus effected, this important member of this meter may not only be
made very accurately, but of what is even of greater importance, with the utmost
uniformity. By not passing the metal core entirely through the ball, but projecting
it inwardly from either side, the ball is thus produced with two cylindrical
openings 64, leaving a partition 65, in its centre, which provides a convenient and
rigid base for the attachment of the disc spindle, as shown.
The seventh improvement is in forming shallow grooves 66, in the ball and also
in the periphery of the disc, the object of which is to provide clearance-spaces
wherein particles of sand or other foreign material liable to be forced between the
bearing surfaces, may enter these spaces and eventually work their way out, instead
of being retained to cut and wear the bearings.
The eighth improvement relates to the dial and pointers of the register.
The dial is shown as having a circular face, upon which are arranged a number
of circular graduates, and to be used with each graduate is a pointer, which is so
constructed and arranged that it shall not in any way cover the numerals or indices
upon the face of the dial, the pointer not reaching out to the numerals, but revolving
within a circle bounded thereby; thus as the pointer rotates. all of the numerals or
indices will be exposed to view. In order that the dial may be accurately read, I
construct the pointer with one of its edges 67, straight and radiating from the
centre of its pivot towards the numerals, while the other edge 68, of the pointer is
curved, being shown as curving from its outer extremity to the hub. The inter-
section of the straight edge or radial projection with the hub is sharply nicked, as
at 69, to more clearly define the straight edge.
By this construction, while the figures or other indices on the dial are at all times
fully exposed to view, the pointers being of less radius than the indices and not
reaching out to them, the sharply defined straight edge furnishes a guide to the eye
for accurately reading the numerals; the exact coincidence of the pointer with any
particular graduation, being much more certainly defined than by the ordinary form
heretofore used; as it will be seen that this requires that three points be brought
into alignment, two of which are moving at unequal velocities. In order to further
aid in accurate reading, I arrange the graduating lines so that they will project
inwardly to a considerable extent towards the centre and thus form on the face of
the dial, a series of recesses apparently having an open inner side towards the
pointer, while the other sides are composed of a segment of the circumference of
the enclosing or boundary circle and the two inwardly projecting graduations. I
then arrange in these recesses the numerals or other indices which correspond to
the value of each space which should be given to the pointer during its travel
through any given recess, or from one graduation to the other.
The second general division of the subject relates to the method and means for
controlling the proportional flow and the relation thereof to the measuring
mechanism. That portion of the apparatus now to be described is positively

page_text: operated by the differences of pressure between a plurality of chambers one of
which (hereinafter termed the controlling chamber) receives the discharge from
the measuring mechanism. The result desired to be accomplished is to cause a
positive increase of resistance to the entire flow to follow any decrease of pressure
in the controlling chamber, and nice versa, upon an increase of pressure therein.
Then furthermore, means and conditions are provided whereby the proper operation
of the device as a whole shall not be liable to disturbance in its proper function by
changes in the velocity of flow.
The entire proportional valve-device is contained in the main external casing 15.
The positive-pressure piston 71, operates in the cylinder 72, of the valve-casing 14;
chamber J, of which is placed in direct communication with the main inlet
chamber K, by the opening 73. The valve 74, which is an open ring supported on
its hub by arms 75, operates in a cylinder 76, which opens its full capacity directly
to the main outlet chamber M. The negative pressure piston 77, operates in the
intermediate cylinder 78, the forward end-closure of which is effected by fixed
partition 79, through a bearing in which the valve spindle 80, freely operates.
The intermediate chamber N, of the valve-casing is suitably connected, as by the
opening 81, to the separate controlling pressure chamber P, while the negative
chamber R, is connected to the main outlet chamber by a channel, as 82, through
the valve spindle and the lateral openings 83, connected therewith. The object of
supporting the valve by the arms 75, is that the water may be free to displace from
one side to the other of the valve. The positive-pressure piston 71, is in fact a
plunger extending outwardly from the negative pressure piston 77; the area of
the positive piston being less than that of the negative, and these pistons taken
together might properly be termed a differential piston. The object of the
channels 82 and 83, is to permit the free displacement of water to and fro between
chambers R and M. The piston, the valve, and the spindle are all connected
together as shown, to act as one part.
The delivery from the main inlet chamber K, to the main outlet chamber M, is
entirely through a series of ports, as 84, 85, radially disposed and preferably formed
in a single transverse plane, as line C, ot the outlet cylinder 76, of the valve casing.
In the drawing two of these ports 84, provide direct communication between the
main inlet and the outlet chambers, (arrows d), while the remaining port 85, pro-
vides communication between the controlling chamber and the main outlet chamber
only, (arrow). The controlling chamber is connected by the opening 86, to the
vertical outlet space 40, of the measuring mechanism, while the receiving chamber 1,
of the measuring mechanism is connected by the opening 32, directly to the main
inlet chamber K. As the areas of the several ports are equal each to the other
the presumptive ratio, therefore, of the measured to the entire volume is as 3: 1.
From the foregoing it will now be seen that all of the ports will be controlled by
the single valve 74; that two-thirds of the whole volume will pass directly from
the outside to the inside of the valve casing, while the final third portion will first
pass through the opening 32, then through the receiving and disc-chambers of the
measuring mechanism, next by the channel 40, and through the opening 86, to the
controlling chamber P, then through the port 85, to the outlet cylinder of the valve-
casing, and thence will pass on with the quantities received through ports 84, as an
integral part of the entire volume.
-
I will give numerical values to the areas of the positive and negative pistons, as
in this wise a more ready comprehension is derived of the operation of the device.
Thus, assume the area of the positive piston 71, to be 100 square inch and the
effective area of the negative piston 77 to be 2.00 square inches; whence the
difference between the piston faces is, 2.00 1001 square inch, the excess of
area of the negative piston over that of the positive.
The operation is as follows: Assume the valve in the position indicated by the
full lines of Fig. 1, in which the ports are partially closed, and that an increased
draft is made causing an increased difference or pressure between the main inlet
and outlet chambers K and M. Then suppose the difference of pressure thus

page_text: produced between these chambers to equal 1 pound to each square inch; whence
1 pound will be exerted upon the positive piston, tending to force the valve
forward.
Meantime pressure will also have been transmitted through the measuring
mechanism, to the controlling chamber, and thence through the opening 81, to the
intermediate chamber N, of the valve casing. The extent of the pressure which
will reach the controlling chamber, to each unit of surface, will be equal to that of
the main inlet chamber less the power absorbed in passing through the channels
and in operating the measuring device. Assume this absorption of pressure in
passing from chambers K, to P, as equal to 0-25 pound to each square inch;
then the effective pressure, to each unit of surface, transmitted into the controlling
chamber will be, 1-0 - 0-250-75 pound, whence, the sum of the power exerted
upon the negative piston to force the valve backward will be, 2 x 0.75 1.50 pounds.
Consequently, as the sum of the power exerted upon the negative piston is greater
by 0.5 pound than that exerted upon the positive piston, the valve will in fact be
moved backward, causing it to open the ports; which action will continue until the
opposing forces are balanced, that is to say, when the sum of the pressure upon
the faces of the pistons (not the pressure upon each unit of surface) will be equal
to the other. During such action, water will flow from chambers P to N, and be
displaced from R to M.
=
Again, if after such a condition of equilibrium has been established, there shall
from any cause be an increase of resistance to the flow through the measuring
mechanism, this will decrease the pressure both in the controlling chamber and
also in the intermediate chamber. The further effect of such obstruction, in
consequence of decreasing the delivery into the controlling chamber, will be to
increase the pressure in the main inlet chamber. Therefore, as the sum of the
power upon the negative piston is decreased, while that upon the positive piston
is increased, the valve will be driven forward, causing it to throttle all of the
ports; which action will be continued until another position of equilibrium will
have been established, as before, between the opposing forces.
During any movement of the valve the fluid which enters or is displaced from
chamber R, passes, as already stated, through the channel in the spindle to or from
the main outlet chamber. Hence, the said chamber R, is negative to chamber N;
the pressure in the said chamber R, being practically identical with that in the
main outlet chamber. In fact, at rapid rates of flow, the pressure in chamber R,
may be less than that of the main outlet chamber, owing to induction due to the flow
past the end of the spindle; which is projected well forward, as shown, towards the
main outlet chamber to prevent any re-active effect from reaching the negative
chamber R.
From the foregoing it will be seen that the position of the valve with respect to
the ports is a resultant of the following conditions, namely: the pressure in the
main inlet chamber K, the pressure in the main outlet chamber M, the pressure in
the controlling chamber P, and the pressures in the several chambers of the valve-
casing. Furthermore, that any fluctuations of pressure in the controlling chamber
alone will result in a co-action of pressure in each and all of the chambers; the
immediate consequence of such co-action being to cause the valve to throttle, to a
greater or lesser degree, all of the ports, in any instance when the pressure in the
controlling chamber decreases; and to cause the valve to open all of the ports, to
a greater or lesser degree, when the pressure therein increases. In other words,
the power absorbed in overcoming the hydraulic and mechanical friction necessary
to the operation of the measuring mechanism creates a difference of pressure,
which acts as a balance or governor to determine the relative position of the valve
with respect to the ports.
In the drawings, I have shown a spring 87, which may be employed to co-act
with the pressure upon the positive piston. It has also another function, which is,
in the event of suddenly stopping a rapid flow of water, this might leave the ports
open, but with the spring as an auxiliary this could not occur, as the spring would

page_text: force the differential pistons and valves forward and close the ports. The employ-
ment of the spring, or its equivalent, (as a weight) in no wise affects the
described operation of the device, as it but increases the intensity or difference
of pressure between the main inlet and controlling, chambers and that of the main
outlet chamber.
Means are also provided for still further compensating or balancing the hydraulic
conditions, consisting of the circular rib 8, formed transversely in the main
casing, leaving an annular space or spaces 89, bounded by the inner edge of the
rib and the valve casing. The function of these ribs is to restrict or throttle
the flow from that portion of the main inlet chamber, which is connected to the
measuring mechanism, and the forward portion which supplies the ports 84, as see
arrow i. By a proper relative proportionment of the areas of the spaces 89, it will
be evident that the water may be delivered under practically identical conditions
as to pressure where leading to the ports 84, and also to port 85. And obviously,
the more nearly this can be accomplished without mechanical intervention, the more
accurate will be the action of such devices as may be employed.
I prefer to situate the valve-casing in the axis of the main casing, as the most
compact construction is thus obtainable, the diameter of the main casing requiring
to be but a trifle greater than that of the supply pipe with little or no complication
in casting the parts. In this wise, too, the machining operations are exceedingly
simple, consisting only in boring a cylindrical bearing lengthwise of the main casing
and adapting the valve casing thereto.
The function of the screw 90, is to prevent the valve-casing from being forced
out of its bearings by pressure.
I prefer to form the ports circular, as shown, by simply drilling a series of holes
through the valve casing, whose number shall preferably correspond to the desired
proportional ratio, as in this manner, the ratio as between a nuniber of meters may
be obtained with the utmost uniformity. Then, too the several edges will be
caused to open exactly simultaneously; which, while subtending a constant ratio
for every increment of movement of the valve, yet affords but a small total area at
low rates of flow; rapidly but constantly, increasing the area with any increase in
the rate of flow.
The attachment of the measuring mechanism to the main valve casing is
conveniently accomplished by means of the screws 91, applied from the interior of
the lower disc chamber casing. There are, however, no great difficulties in the
way of casting the lower disc chamber casing and the main valve casing together
as one part. But there are some advantages in the present arrangement in the
more ready adaptation of these parts to machine processes.
The controlling advantages derived from this construction and disposal, yet
remain to be pointed out, and may be thus summarized: By thus ejecting the
volume from the main inlet chamber and from the controlling chamber in a series
of jets which converge in the accurately finished cylinder of the valve casing, one
jet impinging against another, all finally reacting and passing on through the pipe
as one volume, as see arrows d, e, a perfectly balanced condition of flow is obtained
and that too, at the precise place and instant where the proportional control is
effected. This is a most important feature, as I have found that many heretofore
apparently inexplicable fluctuations in the performance of proportional meters were
caused by the erratic effects produced by currents of different velocities. This I
may illustrate in the instance of two jets discharged under equal pressure past a
valve from inside to outside of a casing; one jet impinging against a fixed con-
tiguous wall, the other jet ejected in the general direction of flow. In the former
instance a considerable portion of the kinetic energy would be absorbed by shock
and eddies, while in the latter instance practically all of the energy would be
merged into the common velocity of the main stream.
Obviously such effects will increase, more or less constantly, with the increase in
the rate of delivery and as the velocity through the controlling passages of
portional meters must be relatively high to accomplish one of the special objects
pro-

page_text: sought (compactness), such erratic disturbances make it much more difficult to
maintain an exact proportional measurement by means of automatic apparatus
operated by differences of dynamic pressures. In other words were this not pro-
vided for, there would be a variable condition with which mechanical appliances
could hardly be expected to successfully cope, because such effects establish
different intensities of pressure in the same chamber. But by the present simple
expedient of causing the entire volume to pass from the outside to the inside of the
valve casing, each particle impinging upon another and all subject to precisely
the same deflections, the dynamic condition thus established is nearly, if not quite,
theoretically perfect and will bear a constant relation under all rates of delivery.
In disposing all of the controlling ports, both of the measured and of the
unmeasured quantities in a single plane of the valve casing, all the ports being
governed by the single valve, difficulties of adjustment for "lap" and "lead are
thereby avoided. Then, too, the direction of the flow is toward the centre away
from the casing, and away from the valve; the tendency being to wash the valve
and carry sand or other foreign substances away therefrom. Furthermore, this
feature otherwise very greatly reduces the liability of the pistons to become clogged
or worn, in that there is no flow either to or from any of the valve casing chambers,
except only during a shift of the valve, as it is to be particularly observed that the
positive piston both receives from and displaces back to the main inlet chamber,
arrow that the negative piston both receives from and displaces back to the
controlling chamber, arrow &, while the actual flow is entirely through the outlet
cylinder 76. Thus, if the draft is at a constant rate and an ordinarily constant
frictional condition of the measuring mechanism prevails, then the valve would
stand as if fixed, and the pressure in the valve casing chambers J, R and N, would
be static. Moreover, the entire flow will be stopped should the measuring
mechanism fail to operate and by such failure prevent the measured proportional
part from reaching the controlling chamber, as in such event, pressure would only
be exerted upon the positive piston; which would drive the valve forcibly forward,
closing off all of the ports. Neither can the meter be operated backward, as should
the outlet be applied to the inlet end of a pipe, the pressure would be transmitted
to the chamber R, through the channel 82, which pressure would maintain the
valve in position and the ports would be kept closed.
The modifications in detail shown in Fig. 13, are presented to indicate the
readiness with which the device may be changed in some particulars, without
departing from the spirit and function thereof, wherefor I do not limit myself to
the precise terms and details submitted, to illustrate my invention. It is not
deemed necessary to make any description of these modifications, as the several
details thereof, corresponding to the preceding figures of the drawing, are carefully
indicated by the same reference letters and numerals.
The commercial advantages of this system are of the greatest importance, as its
manufacture involves the construction of but one size of measuring mechanism;
which being adaptable to any size of valve casing simply involves a plurality of
valves and valve-cylinders, suitably standardized as to the ratio of their ports,
whereby to meet the requirements of actual practice. Thus in the drawing, the
measuring mechanism as Z, may be taken as representative of both of the minimum
and of the direct positive portion of the system; or Z and Y, the latter denoting
the full lines of the valve and valve casing, together comprising the next regular
commercial size, embodying the combined system of direct positive and positive
proportional; while, again Z and the dotted outline W, indicate a still larger
capacity.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed, I declare that what I
claim is
1. The main casings forming the disc chamber, frustums mounted in said disc
chamber: a disk sunported in suid frustume chamber below the lower function

page_text: and a vertical inlet between the channel and disc chamber, substantially as
described.
2. The main casings forming the spherical contour of the disc chamber, the
casings being divided on a medium line of the chamber, the lower casing being
provided with the inlet and outlet channels and the chamber below the frustum,
the upper casing being provided with a vertical inlet, the frustums supported in
the casings, and the disc supported in the frustums, substantially as described.
3. The combination of the main casings forming the spherical contour of the
disc-chamber, the concentric flanges to the casings, a recess in one or both of said
flanges the inner and outer face bearing surfaces, and the gum rubber gasket, the
gasket having a cross-section substantially equal to the cross-section of the recess,
but normally of less breadth than the recess, substantially as described.
4. The combination of the main casings forming the disc-chamber, the frustums
mounted in the disc chamber, and disc supported therein, the chamber below the
lower frustum, the vertical inlet and the curved section connecting the inlet and
the chamber, the construction and arrangement being such that the discharge from
the curved section into the vertical inlet is outside of the sweep of the disc,
substantially as described.
5. The combination of the main casings forming the disc chamber, the frustums
and disc mounted therein, the vertical inlet, and the horizontal chamber in the
lower casing, whereby the movement of the water through the horizontal chamber
is in a direction substantially opposite to its delivery into the disc chamber,
substantially as described.
6. The combination of the main casings forming the spherical contour of the
disc chamber, pf the detachable frustums, cylindrical bearings and stop shoulders
formed in the disc chamber supporting the frustums whereby the frustums are
adapted to be applied from the interior of the disc chamber, substantially as
described.
7. The combination with the disc and diaphragm, of the separate controlling
abutment, substantially as described.
8. The combination with the disc, of the diaphragm, and a notch in the disc
opposite to the diaphragm, and a separate controlling abutment, co-operating with
said notch, substantially as described.
9. The disc ball having openings and a central partition, substantially as
described.
.
10. The disc having grooves in its surface, substantially as described.
11. The ball having grooves in its surface, substantially as described.
12. The combination of the free controlling block, and its cylindrical journal
bearing, with the disc-spindle, disc and frustums, the block being free to adapt
itself vertically to the position of the spindle, substantially as described.
.13. The combination of the free controlling block, and its cylindrical journal
bearing, with the disc-spindle, disc and frustums, the block being free either to
revolve with the spindle by frictional contact or to remain stationary; substantially
as described.
14. The combination of the intermediate gear and the hubs formed thereon,
the differential gears having annular grooves and the piston, substantially as set
forth.
15. The combination of the free differential gear connected to the stuffing box
spindle, the fixed differential gear directly secured to the casing, the annular
grooves in the differential gears, the intermediate gear freely mounted in the
grooves and the pinion, substantially as described.
16. The dial-pointers, having one edge straight and the other edge curved, the
said pointer not reaching out to the numerals, substantially as specified.
17. The combination with the dial, of pointers having one edge straight
terminating in points and the other edge curved, the extremity not reaching out to
the numerals, substantially as specified.
18. A valve device having piston-sections and a valve adapted to reciprocate in
C

page_text: a valve-casing, having chambers, one an end chamber connected to the main
inlet chamber, another an intermediate chamber connected to a separate controlling
chamber which receive the discharge from the measuring mechanism, and a final
chamber communicating with the main outlet chamber, the piston in the
first chamber being of less area than that in the intermediate chamber, the valve
being actuated by the pistons to open and close the communication with the outer
chamber, substantially as described.
19. The combination of a positive pressure piston acting in a chamber connected
to the main inlet chamber, a controlling chamber, a negative piston, of greater area
than the positive piston, acting in a chamber connected to the controlling chamber,
and a valve acting in a chamber connected to the main chamber, the said valve
controlling the communication with the outlet chamber, substantially as described.
20. A differential piston having one end exposed to the pressure of the main
inlet chamber, and its other end arranged to receive pressure from a controlling
chamber receiving the discharge from the measuring mechanism, the area of the
piston which receives pressure from the controlling chamber being greater than
that of the end exposed to the main inlet chamber, and a valve acting in the outlet
chamber to vary the proportional area of the discharging ports according to the
variations of pressure in the several said chambers, substantially as described.
21. The combination in a meter of a series of chambers and pistons moving
therein, and a controlling chamber receiving a limited portion of the fluid, one
piston receiving the pressure of the inlet chamber, another piston receiving the
pressure from the controlling chamber, and a valve controlling the entire discharge
to the outlet, substantially as described.
22. The combination with the measuring mechanism, main casing, differential
piston valve and valve casing, of the main inlet chamber, the controlling chamber
and the main outlet chamber, the arrangement and construction being such that the
main inlet chamber is connected to the measuring mechanism and to the lesser
piston area, the controlling chamber being connected to the greater piston area to
the outlet from the measuring mechanism and to a valve port in the valve casing,
while the main outlet chamber is connected by a series of ports, controlled by a
valve to the main inlet chamber and to the controlling chamber, substantially as
described.
23. The combination with the main inlet chamber, the inlet and outlet channels
of the measuring mechanism, the controlling chamber and the valve casing
chambers, of the valve device provided with a differential piston, one end connected
to the main inlet chamber, the other end the section of greater area connected to
the controlling chamber, and the valve acting in a ported cylinder, substantially as
described.
24. A valve device having a differential piston and a valve, each operating in
separate chambers, when both the measured and the inferred volumes pass through
but one of the chambers, substantially as described.
25. A valve device having a differential piston and a valve, each operating in
separate chambers, one of said chambers receiving and displacing from and to the
main inlet chamber, another of said chambers receiving and displacing from and to
the controlling chamber, while the third chamber receives from both the main inlet
chamber and the controlling chamber, but delivers into the main outlet chamber,
substantially as described.
26: The combination of the negative piston, valve-casing chambers, and the
main outlet chamber with a connecting channel between one of the valve casing
chambers and the main outlet chamber for the purpose of making the pressure
within said valve casing chamber, negative to the other valve casing chamber,
substantially as described.
27. The combination with the differential pistons, valve casing, main inlet
chamber and controlling chamber, of the valve directly connected to the differential
pistons and actuated thereby to vary the area of the discharging ports, substantially
as described.
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page_text: 28. The combination with the valve, valve casing, main inlet chamber, and
controlling chamber, of the series of valve ports disposed radially in a single
transverse plane of the valve casing, substantially as described.
29. The valve and valve casing, having a series of valve ports disposed radially
in a single transverse plane of the casing, the disposal and construction being such
that the entire flow of both the measured and the inferred volumes is delivered
through the said valve ports from outside to inside of the valve casing, substantially
as described.
30. The combination of the spring with the differential piston, the valve and the
valve casing, the disposal being such that the spring co-acts with the pressure from
the main inlet chamber to force the valve forward towards the main outlet chamber,
substantially as described.
31. The combination with the differential piston and the valve casing, of the
openings for connecting the pressure of the main inlet chamber to the positive
piston of the valve device, substantially as described.
32. The combination with the measuring mechanism and the main casing, of the
valve device and the valve casing when mounted in a cylindrical bearing formed in
the axis of the main casing, substantially as described.
33. The combination with the valve casing and valve therein, of a series of ports,
radially disposed in a single transverse section of the casing, the number of the
said ports corresponding to the proportional ratio of the meter, substantially as
described.
34. The combination with the valve casing and valve therein, of a series of ports
radially disposed in a single transverse section of the casing, each of said ports
being of circular contour, substantially as described.
35. A main inlet chamber, a controlling chamber, a valve controlling a series of
ports communicating with the inlet and the controlling chambers and arranged to
direct the total flow in streams of uniform character, substantially as described.
36. A main inlet chamber, a controlling chamber, a valve, and a series of ports
communicating with the inlet and the controlling chambers, and arranged to direct
the total flow in equal streams converging towards the centre of the flow,
substantially as described.
37. A meter provided with a passage for the main stream and a passage for the
measured stream and means for throttling the main stream to equalize the
resistance to the flow of the streams, substantially as described.
Dated the 19th day of January 1893.
PHILIP M. JUSTICE, Fel. Chart. Inst. P.A.,
55 & 56, Chancery Lane, London, Associate Agent.