Year: 1887

page_text: A communication from abroad by JOHN THOMSON, of Brooklyn, in the County of
Kings and State of New York, United States of America, Mechanical Engineer.
1, 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
this invention 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 oscillating meters for water and other liquids and to the
registers therefor.
The invention consists in the adaptation of the oscillating action of a disc to the
purpose of positively measuring water or other fluids; and second, in such details of
construction generally as to produce a complete meter which shall be of the minimum
size, requiring the least material and involving the lowest cost to construct, and yet,
at the same time, maintaining the elements which shall offer the highest efficience in
point of being practically frictionless, noiseless in operation, accurate, durable and
convenient to manipulate and inspect.
In the drawings illustrating the device,
Fig. 1 is a top plan view, and
.
Fig. 2 is an elevation of the meter complete.
Fig. 3 is a detached transverse section through a portion of the upper pressure cap
and register box on the line C of Fig. 1.
Fig. 4 is a complete top plan view of the interior of the meter, the upper pressure
cap being removed.
Fig. 5 is a vertical transverse section and elevation on the line E of Fig. 1.
Fig. 6 is a horizontal section on line P, of Fig. 5, viewed from above.
Fig. 7 is a vertical transverse section through the disc chamber on line S of
Fig. 6.
Fig. 8 is a detached view of diaphragm.
Fig. 9 is a central transverse section of the disc-chamber, showing disc in perspective.
Price 11d:1

page_text: Fig. 10 is a side elevation of disc chamber, showing the inlet port and outlet
spud.
Figs. 11. 12 and 13 are diagram illustrations of the disc in three different positions.
Fig. 14 is a central transverse section through the disc, ball, roller and adjusting
sleeve.
Fig. 14 is a detached enlarged view of stuffing box spindle.
Fig. 15 is a plan view of the dial and hands of register.
Fig. 16 is plan view of the plate upon which the operating parts of the register
are mounted, the dial having been removed.
Fig. 17 is also a plan view of the main plate, but viewed from the opposite side
of that shown in Fig. 16.
Fig. 18 is a vertical transverse section and elevation on line V of Fig. 16, and
Fig. 19 is a detached detail view of one of the pawls and a diagram of its action.
The oscillating disc or piston 15 is secured to and vibrates with the ball 16, which
may be regarded as a part of the disc, and is borne and controlled by the sockets 17, 18,
formed in the apex of the cone frusta 19, 20, the latter being parts of the upper
section 21, and the lower section 22, producing when joined what will be herein
termed a disc-chamber, having the approximate contour in its outer section, of a
spherical zone. The internal surface of the spherical portion of this disc-chamber
is everywhere equidistant from the centre of the ball and sockets. Were the cones
fully developed the points or apexes thereof would be half the distance of the
thickness of the disc below and above the centre of the ball. Therefore, presuming
perfectly accurate and uniform thickness of disc, true cone frusta, and spherical
contour in the disc-chamber, we shall find contact, during a complete oscillation of
the disc, at all points of its periphery and also two constant lines of bearing upon
the cones, (one line upon the upper cone and one line upon the lower cone) which
thus divide the disc-chamber into two compartments. But these compartiments are
constantly changing rotatively, hence arises the necessity of the diaphragm 23, which
is fixedly secured to the disc-chamber and acts in combination with the disc to
effect a separation of the said disc-chamber into two compartments. The diaphragm
operates in the slot 24 of the disc and also serves to prevent the differential
rotation of said disc, and it should preferably be so situated that the side. against
which the slotted edge of the disc impinges shall be in a plane radiating from
the centre of the ball. The foregoing brief statement fairly covers the state of the
art respecting the general construction of this form of piston and chamber gear up
to the time of the improvements and adaptations therein and now to be described.
The disc is maintained in constant and proper relation to the cones by mounting
a conical roller 25 upon the spindle 26; the latter moving with the ball and disc
and hence describing one circular rotation for two vibrations, oscillations or recipro-
cations (any of which terms are properly applicable to the action) of the disc. The
periphery of the roller acts against the fixed conical bearing 27, the lutter being
preferably formed upon and as a part of the gear plate 28. The roller therefore
is carried in a circular path by the spindle and also revolves upon its own centre.
The best form of the roller and bearing is one in which the apices of the conical
surfaces of the roller would be extended to the centre of the ball; as this obviates
any slip in the contacting surfaces of the roller and its bearing.
The roller is mounted upon the sleeve 29, (Fig. 14) the outer surface of which is
also formed conical; the object of which is to obviate any tendency to thrust the
..roller upward, as would be the case if the roller turned upon a cylindrical bearing.
The sleeve is made with a flange 30, which prevents the roller from wedging, and
the inner part of said sleeve is threaded and screwed to the spindle, as at 31.
The advantages of these features are, that the proper action of the disc is con-
trolled by, á rolling movement, and is therefore practically frictionless; also in that
the relative location of the disc to the cones may be very accurately adjusted by
simply turning the sleeve to any desired position up or down upon the spindle. By
this means also the faces of the disc may be brought out of actual contact with
the cones; hence, and if the periphery of the disc be also of a slightly less diameter

page_text: than the spherical section of the disc-chamber, it
abrasion of its surface, except at the ball and socket.
will consequently act without
Although the disc and ball may be formed solid from a single piece of material,
it has been found preferable to construct it as illustrated in Fig. 14, the ball being
made in hemispherical form and then secured to the disc by the threaded portion 32
of the spindle. The ball is centered to the disc by the shoulders 33, and which do
not come together; thereby ensuring a sharp line of juncture at the surface of the
disc, as 34.
The diaphragm is fixedly secured to one of the sections of the disc chambers, as
shown in Fig. 8; the projections 35 and 36 acting to maintain it in proper vertical
relation. The latter passes through the wall of the section and is riveted thereto on
the outer surface.
Upon and as a part of the upper section 21 of the disc chamber is an annular
vertical flange 37, and upon this are formed the projecting inlet spud 38, and outlet
spud 39.
The lower section 22 of the disc chamber is secured to the web 54 of the upper
section by the flange 40 and screws 41.
The external upper and lower pressure caps 42, 43, are secured by bolts 44,
upon gaskets 45, interposed between the faces of the caps and the edges of the
flange 37.
The arrangement of the ports and water ways, and the direction of the current
through the meter are follows :-
Entering the inlet spud 38 the fluid passes both up and down by way of the
openings 46, 47, in the direction of the arrows 49, filling all the space within the
caps around the disc chamber, which space is designated the pressure chamber. Con-
tinuing, the flow is now direct as indicated by arrows 50, 51, to the inlet port 52,
which is formed equally in both sections of the disc chamber. An additional water
way 53 is formed through the web 54 of the upper section of the disc chamber
the object of which is to assist in the free circulation in any or all directions
around the disc chamber, the current thus passing from the primary openings 46, 47,
both in the direction of the arrows 55, 56, as well as that already noted. The disc
operates in the direction of arrow 57, the fluid in the chamber being expelled
through the outlet port 58 and water way 59 of outlet spud 39.
It will be observed that both the inlet and outlet ports are of very large area as
compared to the size of the openings in the spuds, extending around nearly half
of the circumference of the disc chamber approximating 90°. The limitation to the
size of these ports is best shown in Figs. 6 and 10; the edges 60 of which, when
the disc is either at the top or bottom of the diaphragm, are just lapped by the
periphery of the disc. The said edges 60, of the ports should therefore properly be
in a plane approximating the middle of the disc when the latter is in either of the
positions described.
The upper and lower corners 61, 62, of the ports are formed to very nearly
intersect the juncture of the cones, diaphragm and spherical contour of the disc
chamber, see Figs. 11, 12, 13.
The first object of this peculiar arrangement and form of water ways and ports is
to present the greatest possible area of opening to the disc chamber; the velocity of
the current at the maximum capacity of the meter being thereby so greatly reduced
that its dynamic effect upon the disc, ball and sockets is practically inappreciable.
The general trend of the current is also thereby in unison with the oscillation of the
disc, which is favorable to the passage of muddy water or particles of foreign
material. The balance of pressure upon all portions of the disc is also thereby
nearly theoretically perfect; or, expressed in terms, the practical difference between
the + and chambers is that due to the inertia of the disc, the friction of the ball
and socket, and the gearing of the register. Under such conditions it becomes
possible to produce an instrument without extreme refinements of workmanship
giving accurate results at very slow rates of flow, inasmuch as the resistance against
the oscillation of the disc is so slight that it "water packs" by capillary attraction
-

page_text: and operates when the known area of opening around the disc is many times greater
than that of the outlet.
The second object sought is the avoidance of compression of the fluid within the
disc chamber, due to the action of the disc. This is obviated by forming the breadth
of the ports, as between 63 and 64 to at least equal the volume of greatest displace-
ment from one side to the other of the disc.
-
The third object sought is both to avoid confinement of the fluid between the disc
and the cone, at the instant of changing the direction of each distinct oscillation,
and also to prevent communication at this instant between the + and chambers, or
from inlet to outlet direct. This result is attained by constructing that portion of the ports
as shown at 61, 62, and is demonstrated in the diagram, Figs. 11, 12 and 13, which
respectively show the disc, first, just as it nears the end of the downward oscillation,
the corner 62 of the inlet port 52 being slightly open; second, the downward
oscillation terminated and both inlet and outlet corners of the ports closed; third,
the upward oscillation beginning and the reverse corner 62 of the outlet port 58
open. Thus the disc acts as a valve to the ports without confinement or compression
of fluid within the disc chamber.
By the described arrangement of water ways and ports, construction of disc
chamber and pressure caps, the entire working apparatus is suspended in a neutral
chamber having a balance of pressure within and without.
Attention is called to the fact that by this arrangement of water ways and ports,
there is practically no retardation of the flow, the loss of head being simply that due
to the light circular deflection from the original line of introduction, and which is
partially compensated by the increased area and reduced velocity through the meter;
and also that the meter is operative in either direction of flow. But in reversing
the operation herein described the direct impact of the inflowing current would be
against the ball and upon the edge of the disc; the consequence of which would be
the speedy destruction of the machine as an instrument of precision.
The sum of the oscillations of the disc is transmitted to the stuffing box spindle 63°
which is connected to the register by means of the gear train 64 actuated by the
primary pinion 65 and arm 66 fast to the spindle 67; the said arm impinging
against and being driven by the roller.
It is of course evident that other forms of gear trains may be employed to effect a
proper transmission to the register. The novelty of this application consists in
mounting the entire internal train upon the single gear plate 28, and in then securing
the said gear plate accurately and rigidly to the upper section of the disc chamber by
the flange and shoulder 68, the union being maintained by screws, as 69.
The advantages of this construction are that the centre of the conical bearing 27 is
readily formed to lie in the exact axial line as 70, Fig. 7, and at a right angle to the
horizontal plane of the disc chamber; a result of the utmost importance to the truth
of the action of the disc and roller; while the gearing is thus very convenient to
assemble and adjust, being separate and distinct until ready to apply to the disc
chamber.
The gear 71 is fixedly secured to the stuffing-box spindle 63, the said gear
engaging the final pinion 72 of the internal gear train, as see Figs. 4 and 5. This
necessitates bringing the upper pressure cap in proper relation to the disc chamber.
The method pursued is to place the cap in position without applying the packing to
the spindle; which latter is thus left free in its bearing; then, by sliding it back and
forth its proper mesh can be quickly and accurately ascertained when the cap bolts are
fully tightened and the steady pin 73 is next inserted in the upper cap and the disc
chamber, (see Figs. 1 and 2). In this wise the cap may be removed by unskilled
hands and be accurately reset to its former position without readjustment of the mesh
of the gearing.
The stuffing box is formed by the hub 74 threaded on the outer surface, as 75, to
which is adapted the cap-nut 76, the elastic packing material, as 77, being inserted
between the upper surface of the hub and the lower inner surface of the nut. The
stuffing box spindle where it is encompassed by the elastic packing material is of

page_text: special construction, as best shown in Fig. 14, where it is shown as having around it
a plurality of grooves or recesses 78, which pass entirely around the body of the
spindle circumferentially but are distinct and separate from each other.
The effect of this is, that when the elastic material is compressed by the nut it fills
the grooves, contacting both at the bottom and sides thereof, each thereby forming a
distinct obstruction to the passage of fluid. Also the pressure of the fluid against the
packing tends to force it against the sides of the grooves, and to assist in securing a
perfect joint. This construction and arrangement requires but little packing material;
there is little or no tendency to cramp the spindle, and the result is a practically
perfect and frictionless joint.
Attention is called to that fact that, as shown in Fig. 2, the cap-nut may be readily
reached to tighten the same if necessary without disturbing any part of the device.
The register box 79 is secured to the cap by the screws 80, the seal being applied to
the recessed extension S1, as shown in Fig. 3.
The recording register illustrated in Figs. 5 and 15 to 19, is connected to the
stuffing-box spindle by the gear 82 fast to said spindle, and which meshes with the
central driving wheel 83 of the register. In this register the main indexing hands
have a common direction of motion, but the notion of each is intermittent. Its
construction and operation is as follows:-
:-
Upon the plate 84, and bearing directly against the lower surface thereof, are
mounted four toothed wheels, 85, 86, 87 and 88. Fixedly secured to the wheels, and
projecting upward and having a bearing in the said plate, are four studs or pivots 89;
the outer extensions of which carry the short indexing hands 90. On the upper
surface of the plate are four triangular spring washers 91, having a bearing upon the
studs 89, and maintained in intimate contact with the face of the plate by means of
the pins 92 which pass through the studs. Thus the action of the spring washers is to
draw the wheels upward in close contact with the lower surface of the plate,
wherefore the wheels will resist rotation to the limit of the friction produced by the
washer.
Mounted in the journal bearing 93 formed in the centre of the plate is the
spindle 94, of the centre wheel 83 and which carries the unit index hand 95. Fixedly
secured to the centre wheel and projecting upward therefrom is a pin 96, the function
of which is to engage the teeth of the primary toothed wheel 85. Upon the toothed
wheels 85, 86 and 87 are pivotally mounted three pawls, 97, 98 and 99, that is, one
pawl to each wheel. In the pawls are formed cams or slots 100, which are engaged
and guided by the headed pins 101, the said pins being fixedly secured to the plate.
The cams are of such form as to effect a quick engagement and disengagement of the
teeth of the ratchet wheels.
In the operation of the device it is presumed that for each complete revolution of
the centre wheel, the pin 96 will intermesh with and cause the toothed wheel 85
to rotate through a space equal to one of its teeth, or the tenth part of one
revolution.
In the illustration here shown the unit hand indicates up to the sum of 10 in sub-
divisions of tenths, while the smaller hands indicate successively in tens, hundreds,
thousands and tens of thousands, reaching a total reading of 100,000. Consequently
in the combination here assumed each of the toothed wheels require to have ten teeth,
as shown. Ten revolutions of the centre wheel will impart one rotation to the
wheel 85. The effect of this is to produce a complete reciprocating action in the
pawl 97. The outer extensions of the pawls are bent inward, as at 102, the points
coming in contact or nearly so with the lower face of the plate. The reciprocating
action of the pawl 97, causes the point thereof to engage one of the teeth of the
wheel 86, causing it to rotate the space of one of its teeth. Thus it will require ten
revolutions of the centre wheel to rotate the wheel 85 one revolution, while action of
the said wheel 85 by means of the pawl 97 will impart the tenth part of one
revolution to the wheel 86, and in like manner motion will be imparted to the
wheel 87 by means of the pawl 98.
In general. terms, the apparatus just described may be designated a step by step

page_text: gear ramune pawi and cam, with pin operating therein, performing the function or
intermediate gearing.
The arrangement of the several parts is such that when all the hands point to the
numeral 9 of their respective graduates the continued motion of the centre wheel,
carrying the unit hand forward to zero, will cause all of the index hands to operate
together in one common direction of rotation and during the same period of time,
passing from 9 to 0. Thus it is evident that the only opportunity offered for
reading the register in error is limited to the measurement of about one unit;
and this will make clear the object of constructing the pawls in such manner as to
act upon the toothed wheels very quickly and in unison. In the present illustration
the unit hand 95 rotates in an opposite direction to that of the hands 90, but this is
immaterial in practice as the unit hand is read only in testing.
The centre wheel rotates upon a centre 103 eccentric to the centre 104, from
which latter centre are developed the bearings of the toothed wheels, (see dotted
line 105). The object of this is to permit the proper engagement of the pin 96
with the toothed wheel 85 only, as shown by the dotted line 106 representing the
path of the pin. In this wise all the toothed wheels may lie in the same horizontal
plane flush with the plate.
The operation of a toothed wheel by any one of the pawls is effected while the
point of such pawl is travelling from 0 to 1, Fig. 19; which, it will be observed, is a
space greater than that of the pitch of the teeth of the toothed wheels. In this wise
there is no nicety of adjustment required, the point of the pawl carrying its
corresponding toothed wheel the proper distance and then passing back free.
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 by my foreign correspondent, I declare that what I claim is:
1. The combination with the disc chamber and the oscillating disc of the rotating
roller acting upon a fixed bearing.
2. The conical roller and corresponding conical fixed bearing in combination with
the oscillating disc and disc chamber.
3. The gear plate, upon which is formed the conical bearing, in combination with
the disc chamber, oscillating disc and roller, for the purpose specified.
4. The combination with the disc chamber and oscillating disc contained therein, of
the gear plate carrying a conical bearing upon its under side and having mounted
on its upper side the internal gear train of the registering mechanism, the said plate
being detachably mounted upon the outside of said chamber.
5. The combination with the external pressure caps, of the disc chamber and
oscillating disc operating therein, the said chamber having ports and water ways,
substantially as described, whereby the current flows directly from the opening in the
spud to the chamber formed by the pressure caps above and below the outside of the
disc chamber and thence passes within and through the said disc chamber.
6. The combination with the outer chamber of the sections of the disc chamber
having a port 52 formed equally in both sections.
7. The combination with the disc chamber and disc therein, the chamber having
the ports 52, 58, the upper and lower edges of which extend circumferentially around
the disc chamber to or about 90 degrees, substantially as described.
8. The combination of the disc chamber, consisting of sections 21 and 22, the
stationary diaphragm, the oscillating disc enclosed in said disc chamber, the said disc
chamber being provided with ports 52 and 58, and the pressure chamber, one of said
ports opening directly to the spud or pipe and the other of said ports opening to the
said pressure chamber, substantially as described.
9. The combination with the disc chamber, disc, spindle, roller and fixed conical
bearing, of the conical sleeve 29, for the purpose set forth.
10. The combination with the disc chamber, disc, spindle, roller and fixed conical
bearing, of the conical sleeve 29, having a flange 30, for the purpose set forth.
11. The combination with the disc chamber, disc, spindle, roller and fixed. conical

page_text: bearing, of the conical sleeve 29, adapted to be adjusted back and forth upon said
spindle, for the purpose of bringing the periphery of the said roller in proper relation
to the said fixed conical bearing.
12. The combination of the disc, threaded spindle and hemispherical sections as
described and shown.
13. The diaphragm having the projections 35, 36, one of which is adapted to pass
through the wall of the disc chamber and to be riveted thereto, substantially as and
for the purpose specified.
14. In a water meter, the combination with the internal gear train, the stuffing box
spindle having a gear wheel connected therewith, the upper pressure cap and disc
chamber, of the steady pin 73, whereby to permit the withdrawal and accurate
replacement of said cap, as herein set forth.
15. The stuffing-box spindle, having the circumferential grooves as 78, for the
purpose specified.
16. The combination with primary operating mechanism, as the gear 83, and pin 96,
of the toothed wheel, as 85, the pawl pivotally mounted thereon, the cam formed in
the pawl, a fixed pin engaging the cam, and a corresponding toothed wheel, as 86,
arranged to be engaged by the point of the pawl and to be rotated intermittently
thereby, substantially as described.
17. The combination in series, of a plurality of toothed wheels each carrying a
pawl, pivotally mounted, having a slot or cam, engaged by a fixed pin, the point of
each pawl acting upon the teeth of the contiguous wheel, whereby upon the complete
revolution of any one wheel carrying a pawl the next wheel of the series will be
rotated through a space equal to the pitch of one of its teeth, substantially as
described.
18. The pawl, having a cam, as 100, in combination with the wheel upon which it
is pivotally mounted and by which it is actuated, the fixed guide pin as 101, and a
toothed wheel to be operated by the tooth of the pawl, substantially as described.
Dated this 21st day of December 1887.