Year: 1886

page_text: I, OLIVER IMRAY of No 28 Southampton Buildings, 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:-
My invention relates to governors for steam engines, water wheels and circular
motors, and the purpose whereof is to provide an apparatus whereby an accurate
differential adjustment shall be given to the valve or gate through which the
vapour or fluid passes to the motor; wherein the adjusting devices shall be driven
by positive mechanism, and the entire mechanical organization be greatly simplified
and reduced in bulk.
The invention consists in the several novel features of construction and combi-
nations of parts hereinafter fully set forth and definitely pointed out in the claims
annexed to this specification.
In the accompanying drawings Fig. 1 is a vertical section in the plane 1-1,
Fig. 2 shewing the casing with its interior mechanism, the cylinder head being
removed.
Fig. 2 is a central vertical section of Fig. 1 taken in the plane of the axis of the
common shaft.
Fig. 3 is a side elevation of the parts shown in Fig. 1, part of the cylinder shell
of the casing being removed.
Fig. 4 is a side elevation of the closed casing, shewing the driving shaft with its
pulley, and the adjusting gear sleeved thereon, at the opposite end of the shaft.
Fig. 5 is an end elevation of the closed casing taken from the right of Fig. 4.
In the said drawings the reference numeral 1 designates the casing within which
the operative parts are assembled. This casing is preferably made in cylindrical
form, as shewn, for the purpose of giving compactness and reducing the bulk, but
otherwise it forms no essential feature of my invention. An angle plate 2 is cast
upon the lower portion of the casing and strengthened by a central rib 3, crossing
the bottom of the cylindrical shell 4. This angle plate not only forms a convenient
means of attaching the casing to a suitable support, but it also serves as a mounting
for a post 5, carrying a journal box 6 for one end of the central shaft.

page_text: The cylindrical casing or shell 4, is divided upon a central horizontal plane, into
two equal parts, or sections, as shewn in Figs. 3 and 4, but the casing may be
divided in any other suitable manner.
Through the casing and coincident with its cylindrical axis, is passed a shaft 7,
having its bearing in sleeves 8 and 9, mounted upon or near each end of the shaft.
These sleeves are supported in journal boxes 10, cast integral with the cylinder
heads, and each has revolution independently of the movement of the shaft 7.
Centrally mounted upon said shaft 7 and rigid therewith, is a hub 11, and
projecting radially from opposite sides thereof are two tubes 12, tapped into said
hub and containing in each a spiral spring 13, attached at the end nearest the shaft,
to rigid pins 14.
Sleeved upon each of said tubes 12 is a mitre gear 15, having a hub 16, which
is prolonged outwardly, as shewn in Fig. 2. Surrounding these prolonged hubs
or sleeves are cylindrical caps 17, which rest upon the hubs of friction
gears 18
spliced upon the prolonged hubs 16, and not only having revolution therewith, but
being capable of radial adjustment upon the same, by the means presently to be
described. Upon the outer end of each tube 12 is turned a threaded secrew
section 19, by which each mitre gear 15 is held down upon a boss 20, formed upon
the hub 11, each of said tube sections 19, being outwardly flush with the prolonged
hubs 16. Passing through the outer ends of the cylindrical caps 17, are rods 21,
connected to the outer extremities of the springs 13, and upon the exterior threaded
ends of these rods are turned nuts 22, held by jam nuts 23. By this construction
it will be seen that, while the friction gears 18 must turn with the mitre gears 15
they may, at the same time, under a sufficient centrifugal force, be projected out-
wardly upon the prolonged hubs 16, upon which they are spliced, when the
centrifugal force producing this movement is expended, the gears 18 will be
returned to their original position by the tension of the springs 13. The cylin-
drical cap 17 moves freely outward, and inward, relatively to the shaft 7, but is
prevented from turning by means of pins fixed upon the tube sections 19, and
engaging with slots cut longitudinally in the inner faces of said cap.
Mounted or formed upon the inner end of the sleeve 9 is a double gear composed
of a mitre gear 24, of such diameter that it meshes with both of the mitre gears 15,
and a gear 25 concentric with, and lying in the same vertical plane with an
internal gear 26, rigidly mounted upon the cylinder head. The diameter of the
internal gear is twice that of the gear 25, and between the two, upon opposite
sides of said gear 25, are placed planet gears 27, meshing with both, and having
upon their axes, arms 28. which are rigidly attached to the hub 11. Upon the
outer extremity of the sleeve 9 is mounted a pulley 29, by which rotation is imparted
to the gear 25, and the mitre gears 24, said pulley being driven by a belt from any
suitable part of the mechanism driven by said motor.
Upon the sleeve 8 is spliced a disk 30, having a diameter in excess of that of
the friction gear 18, said disk being held in frictional contact with the gears 18 by
means of springs 31, interposed between a flange 32 upon the sleeve 8, and the
hub of the friction disk 30. By the construction and combination of parts hereto-
fore described, it will be seen that the hub 11, will be caused to revolve about the
shaft 7, carrying with it the gearing mounted upon the tubes 12, and it is also
evident that the double gear 24 and 25 will accomplish two revolutions while a
hub 11 is making a single rotation. This is due to the fact that the planet.gears 27
being one half the diameter of the gear 25, the latter will revolve them twice to
one of its own revolutions, but as said planet .gears also mesh with the internal
gear 26, which being twice the diameter of gear 25, is therefore four times the
diameter of said planet gears, the latter must make four revolutions upon their
own axes to pass once around the internal gear. To cause these four revolutions
and to produce therefrom one complete revolution of the hub 11 with its attendant
gearing, the gear 25 must evidently make two revolutions.
As the gears 24 and 25 make two revolutions about the common axis 7 to one
made about the same axis by the gears 15, it follows that the gear 24 will cause

page_text: gear 15 to revolve once upon its own axis in the same time; i.e. it will revolve
once upon its own axis while the bearing upon which it is mounted revolves once
about the common axis 7. Now it is evident that, if the friction gears 8 have
bearing upon the disk 30 at a distance from the axis of the shaft 7 equal to the
diameter of the gears 18, the latter will merely have rolling contact with said disk.
In other words, let it be assumed that the friction gears 18 have a radius of
four inches, and consequently the diameter of eight inches, their circumference will
measure 24 inches, +, -, If now said gears have contact with the disk 30,
at a point four inches from the axis of the shaft 7, and make a single turn upon
their own, axes while the bearing upon which said axes turn makes a single
revolution upon the common axis 7, the gears 18, which are driven, as already
shewn, by positive mechanism, will simply roll upon the disk 30, and the line in
which they travel may be denominated the neutral point of the disk. If, however,
the speed becomes so great as to generate sufficient centrifugal force to project the
friction gears 18 outward upon their axes, until they travel in a circle beyond said
neutral point, then said gears will impart at each rotation a movement to the
disk 30, proportioned to the difference between the circumference of said disks
and the larger circle on which they travel, thereby carrying said disk in the
direction in which they travel. For example, if the friction gears make contact at
a point on the disk 30 distant radially five inches from the axis of the disk, then
at each revolution of the shaft 7, and of the gears 18, the disk will receive a
movement in the direction travelled by the friction gears of about six inches,
meausured upon the circle of contact, the equation being substantially (letting x
represent the difference between the circumference of the gears and the line of
travel) 10 × 3.14159 8 × 3.14159 IC. Or, performing the operations
indicated, it will be found that the disk 30 will move with the gears a distance of
6.283 inches, meausured upon the circle of contact.
On the other hand, let it be supposed that the speed is so far decreased as to
allow the tension of the springs 13 to draw the gears 18 inward, toward the
shaft 7, to a point say three inches of radial distance from the axis of said shaft.
In this case, the relative speed of the gears being a constant quantity (as well as
their travel about the common axis 7) the disk 30 will be revolved in the opposite
direction, its degree of movement being equal to the difference between the cir-
cumference of the actuating gears and the circle of contact. Letting represent
the relation of the perimeter to the diameter of each, the equation will then read
(letting represent the difference as before) 8 × = 6 x + x, or in other
words, the disk 30 will receive a motion opposite to that of the friction gears equal
to 6.223 inches for each revolution of the said gears, said distance being measured
upon the circle of frictional contact.
Upon the outer extremity of the sleeve 8 is mounted a mitre or roller gear 33,
by which movement may be given to the device, by which the steam port or water
gate is opened and closed. Now by applying to the described mechanism the
explanation given above, it will be seen that, if the speed of the motor increases,
either suddenly or slowly, the friction gears will be projected outward upon their
bearings, against the inward draft of the springs 13, a distance proportioned to the
centrifugal force developed by such increase in speed, thereby carrying the gears 18
beyond the neutral line upon the disk 30, and causing a movement of the latter
upon its own axis which will gradually close the port and diminish the flow of
steam. If, on the other hand, the speed falls below the average required, the
tension of the springs 13, will draw the gears inward toward the common axis 7,
giving frictional contact upon the disc 30, within the neutral circle, and producing
at each revolution of the gears, a movement of the disk, and consequently of the
gear 33 whereby the port will gradually be opened and an increase of motive
power applied.
The device actuated by the disk 30 may be a train of gearing meshing with the
gear 33, or a simple rack bar, meshing with a spur gear upon the sleeve 8.

page_text: I have indicated upon the disk 30 the neutral point of contact for the gears 18,
by a line designated by the letter a. If the centrifugal force is sufficient to project
the gears beyond this point, the disk will move with said gears, as already
described but if the speed is so far diminished as to bring the gears within said
point, the disk will be driven in the opposite direction. By adjusting the tension
of the springs 13, by means of the nuts 22 and 23, the apparatus may be adapted
to any load and to maintain a given speed under all circumstances.
Having now particularly described and ascertained the nature of my said
invention and in what manner the same is to be performed, I declare that what
I claim is
1. In a governor for motors, the combination with a disc having independent
bearing, of a friction gear or gears, bearing thereon, bearings radiating from the
axis of the disc bearing, upon which said gears are adjustable longitudinally, said
bearings being mounted upon an axis coincident with that of the disc, mechanism
for imparting to said friction gearing and to the bearing upon which it is mounted,
synchronous rotation of said mechanism being adapted to open and close a steam
or other port by devices actuated by the revolution of said disc in opposite
directions, substantially as described.
2. In a governor for motors, the combination with a disc opening and closing the
port of the engine, of friction gears bearing upon the flat face of said disc, radial
bearings upon which said friction gears are rotated and adjusted, a shaft carrying
said bearings and having synchronous revolution with the friction gears and
springs drawing said gears toward the axis about which their bearings rotate,
substantially as described.
3. In a governor for motors, the combination with a shaft driven by any suitable
means of a hub rigid thereon, tubes projecting radially from opposite sides of said
hub, miter gears sleeved upon said tubes and having prolonged hubs held in place
by nuts on the threaded ends of the tubes, friction gears spliced upon said pro-
longed hubs, springs drawing said gears toward the revolving shaft, a friction disc
sleeved on said shaft, with the plane face of which the friction gears engage, and
means for imparting to the shaft and to the said gears equal revolution in equal
time, substantially as described.
4. In a governor for motors, the combination with a disc journalled upon an
independent axis, of friction gears engaging with the plane face of said disc,
rotating bearings upon which said gears are radially adjustable and means for
imparting to said bearing or to the gears mounted thereon equal and synchronous
revolution in planes substantially at right angles to each other, substantially as
described.
5. In a governor for motors, the combination with a revolving shaft and a hub
rigid thereon of tubular bearings radiating from said hub, miter gears sleeved upon
said bearings, friction gears spliced upon the prolonged hubs of said gears, a disc
with the plane face of which the friction gears engage, a miter gear meshing with
the miters upon the tubular bearings, a spur gear carried by the miter gear, a
stationary internal gear in the same plane with the spur gear, and planet gears
meshing with said spur and internal gear and rigidly connected with the hub upon
the shaft, substantially as described.
6. In a governor for motors, the combination with a friction gear spliced upon
the prolonged hub of an actuating gear, of a bearing for the latter mounted radially
upon a rotating axis, a spring drawing said friction gear toward the rotating axis,
a disc with the plane face of which the gear engages and gearing whereby the
friction gear receives a single rotation upon its bearing to each rotation of the axis
carrying said bearing, substantially as described.
7. In a governor for motors, the combination with a friction gear splice: upon
the prolonged hub of an actuating gear, of a bearing for the latter mounted
radially upon a rotating axis, a spring drawing said friction gear toward the
rotating axis, means for varying the tension of said spring, a disc with the plane

page_text: face of which the friction gear engages, gearing whereby the latter receives a
single rotation to each rotation of the axis carrying its bearing, and devices
actuated by the disc, for opening and closing the steam port, substantially as
described.
8. In a governor for motors, the combination with a rotating support of tubular
bearings rigidly mounted thereon and containing spiral springs, miter gears
revolving upon said tubular bearings and having prolonged hubs, friction gears
spliced upon said hubs and drawn by the springs toward the axis of the rotating
support, a disc with the plane face of which the friction gears engage upon opposite
sides of its axis and gearing for giving equal rotation in equal times to the friction
gears and the support carrying the tubular bearings, substantially as described.
9. In a governor for motors, the combination with a disc, with the plane face of
which friction gears engage upon opposite sides of its axis, of a spring coiled upon
the sleeve of said disc and forcing it against the friction gears, bearings upon
which the latter revolve, a rotating shaft carrying said bearings, and means for
imparting to said shaft and to the friction gears equal rotation in equal times,
substantially as described.
10. In a governor for motors, the combination with a stationary internal gear,
and a concentric spur gear, of planet gears meshing with both a sleeve carrying
said spur gear and a miter gear and driven by suitable means, miter gears meshing
with the miter on the sleeve and mounted on tubular bearings carried by a hub
which is rotated by arms connected with the planet gears, friction gears spliced
upon the prolonged hubs of the miters, springs coiled within the tubular bearings
and drawing the friction gears toward the axis of the hub, devices for adjusting
the tension of said springs, a disc with the plane face of which the friction gears
engage, a sleeve on which the disc is mounted, a spring bearing on the rear face of
the disc, a common shaft carrying the sleeve of the disc and of the actuating miter
and spur gears and gearing carried by the former sleeve and actuating the devices
for opening and closing the port of the engine, the parts being so proportioned that
the friction gears revolve upon their axes in equal time with the revolution of the
hub carrying the tubular bearings substantially as described.
Doted this 19th day of Tonu 1000
ABEL & IMRAY,
Agents for the Applicant.