Improvements in Steam or other Fluid Pressure Engines.
Year: 1891

page_text: Date of Application, 18th Aug., 1891-Accepted, 3rd Oct., 1891
COMPLETE SPECIFICATION.
[Communicated from abroad by ELMER STILLMAN SMITH, of Boundbrook,
Middlesex, New Jersey, United States of America, Mechanical Engineer.]
Improvements in Steam or other Fluid Pressure Engines.
1, HENRY HARRIS LAKE, of the firm of Haseltine, Lake & Co., Patent
Agents, 45 Southampton Buildings, in the County of Middlesex, 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 an engine which is provided with a disc or piston
having a peculiar wobbling motion, partly oscillating and partly rotative and
which is arranged in a case or chamber having the form of a spherical segment.
The objects of my invention are to increase the efficiency of the engine, to
facilitate the adjustment of the parts, to reduce friction, to render the automatic
governor very sensitive, when a governor is employed, and to improve the cut-off
and reversing mechanism, when the engine is of the reversible type.
In the accompanying drawings
:-
Figure 1 is a longitudinal sectional elevation of my improved engine.
Figure 2 is a longitudinal section of the main bearing, on an enlarged scale.
Figure 3 is a side elevation of the bearing.
Figure 4 is a side elevation of the notched ring which carries the rollers of the
main bearing.
Figure 5 is a longitudinal sectional elevation of the case and piston through
the ports of the piston and valves, the plane of section being in line xx,
Figure 8.
Figure 6 is a top plan view of the case and piston, partly in section, the view
being taken at right angles to the line -, Figure 8.
Figure 7 is a fragmentary face view of the piston, on an enlarged scale, showing
a cross section of the valves in line a-x, Figure 5.
Figure 8 is a face view of the piston.
Figure 9 is a longitudinal sectional elevation of the lower portion of the case
and piston.
Figure 10 is a bottom view of the lower jointed division plate with the adjoining
portions of the piston in section.
Figure 11 is a perspective view of the main portion of the jointed division
plate.
Figure 12 is a perspective view of the wing of the jointed division plate.
Figure 13 is a side elevation of the packing strip of the jointed plate.
Figure 14 is a bottom view thereof.
Figure 15 is a bottom view of the detachable head of the packing ring.
Figure 16 is an edge view thereof.
Figure 17 is a longitudinal section of the rigid division plate.
Figure 18 is a top view thereof, showing the adjoining part of the case in plan
view and the adjoining part of the piston in section.
Figure 19 is an end view of the rigid plate.
Figure 20 is a top plan view of the packing strip of the rigid division plate.
Figure 21 is an end view of the hollow follower pin.
Figure 22 is a longitudinal sectional elevation of the crank disc and connecting
parts.
Figure 23 is a cross section of the roller bearing of the wrist pin in line x-,
Figure 22.

page_text: Figure 24 is a rear elevation of the crank disc and the governor mechanism
attached thereto.
Figure 25 is an edge view of one of the governor weights.
Figure 26 is a' side elevation of the main valve with the roller bearing of the
cut-off valve in section.
Figure 27 is a cross section in line x-x, Figure 26.
Figure 28 is an end view of the carrier by which the main valve is rotated.
Figure 29 is a cross section in line y-y, Figure 26.
Figure 30 is a side elevation of the cut-off valve.
Figure 31 is a cross section in line a-x, Figure 30.
Figure 32 is a longitudinal sectional elevation of my improved engine provided
with a reversing mechanism.
"
Figure 33 is an end elevation of the reversing lever and connecting parts.
Figure 34 is a fragmentary longitudinal section of the engine on an enlarged
scale.
Figure 35 is a cross section of the spherical cap surrounding the wrist pin, in
line -a, Figure 34.
Figure 36 is a longitudinal section of the rear portions of the valve stems and
connecting parts.
Figure 37 is a cross section in line x-x, Figure 36.
Figure 38 is a longitudinal section through the cut-off segment arranged in the
valves.
Figure 39 is a rear elevation of the carrier plate attached to the stem of the
main valve.
Figure 40 is a rear elevation of the collar attached to the stem of the cut-off
valve.
Figures 41, 42, 43, 44 and 45 are rear elevations of the carrier plate of the main
valve in different positions of the valves.
Figures 46, 47, 48, 49 and 50 are cross sections of the valves, showing the same
in corresponding positions.
In Figures 1 to 31, my inventions are illustrated as embodied in an engine
provided with an automatic governor. In these figures, A represents the case
in which the piston works and which has the form of a spherical segment.
A' represents the head which is secured to the large end of the case and is provided
with a cylindrical extension A² which is arranged axially with reference to the
case. a represents an annular flange which surrounds the central opening a¹
formed in the crown of the spherical case and by which the latter is secured to
the steam chest B which receives steam through the supply pipe. The steam
chest is preferably cast integral with the engine frame B' which supports the
engine shaft B² by means of a main bearing B³ adjoining the steam chest and an
end bearing B. The pulley B' or other device by which power is transmitted
from the engine shaft is preferably secured to the latter between the bearings.
The engine shaft is arranged axially in line with the case A and carries within
the steam chest a crank dise C which may be cast integral with the engine shaft
of steel.
D represents the piston having the form of a spherical segment and fitting with
its spherical back in the spherical case, while its face is made convex, so that, as
the piston is arranged obliquely in the case, the piston fills the case only partially
and leaves a steam space between the receding portion of its face and the head A¹
of the case.
E represents a follower pin or knuckle which is arranged in the cylindrical
extension A2 of the head A¹ and projects with its semi-spherical inner end into
the case where it seats itself in a correspondingly shaped recess or depression in
the face of the piston. This pin is made hollow and has at its apex an opening e
through which the exhaust steam enters the cavity of the pin from which it
escapes through the open outer end of the piu into the extension A² which latter
is provided with an exhaust pipe e'. The pin is adjusted longitudinally to take

page_text: up wear by an adjusting screw e² which passes through a threaded opening in the
head at the outer end of the extension A². This adjusting screw is connected
In order
with the follower pin by a reduced neck e* and head e, Figures 1 and 5.
to simplify the connection of the adjusting screw to the follower pin, the hub at the
outer end of the latter is provided with a notch e, Figure 21, which receives the
reduced neck, while the head bears against the inner side of the hub and
the shoulder of the screw against the outer side of the hub. This connection permits
the follower pin to swivel on the adjusting screw and enables the pin to change its
position in the casing by a rotative motion, thereby equalizing the wear.
F and F represent the division plates or abutments which are attached to the
head A' of the case and project across the steam space into pockets formed in the
piston. Two or more of these division plates are employed, four being shown in
the drawings. When four of these plates are employed two of them, arranged
diametrically opposite each other, are preferably rigid plates which have a pivoted
or rocking connection only with the head A¹ of the case, while the other plates
consist each of two parts which are connected by a flexible joint or radial pivot,
whereby the plates are better enabled to follow the wobbling motion of the piston
and binding is prevented. In the drawings, F represents a solid or rigid plate
which is arranged in the upper part of the case, as represented in Figure 1, and
F represents the jointed plates which are arranged in the lower part of the case and
at the side thereof, so that one rigid plate and three jointed plates are represented,
which arrangement is, however, less preferable than that in which two rigid plates
and two jointed plates are used. The rigid plate holds the piston in position and
prevents it from turning so far as to cramp the jointed plates, while the latter by
their flexibility adapt themselves to the position which the piston is compelled to
assume by the solid plate.
Each of the plates F and F is connected with the head A¹ by a tapering
knuckle which enters a similarly shaped seat f¹ in the inner face of the head.
This knuckle has the form of a steep-truncated cone, the apex of which is located
in the centre of the case. The knuckle is formed on the front end of the plate
and the seat in the head opens rearwardly to allow the plate to project into the
steam space and piston. The sides of the plate are inclined at the same angle as
the knuckle and the sides of the pocket in the piston are similarly inclined, as
represented in Figures 7 and 8, so that wear can be taken up by adjusting the
plates inwardly.
Each of the plates is pressed toward the centre of the case and against the
follower pin by a spring 3 which bears against the outer or circumferential end of
the knuckle and is seated in a socket in the case in which its tension is adjusted
by a screw f, Figure 9.
The solid plate F' fits snugly with its sides against the sides of the pocket of the
piston, Figure 18, except that the rear portion of the socket is slightly enlarged to
reduce the area of the contact surfaces and the resulting friction.
G, Figures 17-20, represents a curved packing strip applied to the outer
circumferential end of the solid plate and seated in a depression which is formed in
the plate and has the form of the strip. The latter is provided near its front end
with a ring-shaped enlargement which exposes the end of the knuckle and permits
the spring to bear against the knuckle within said ring. The packing strip is
provided at its opposite end with a cross bar g' which extends from one side of the
plate to the other. This strip is pressed outwardly against the spherical inner
surface of the casing by the steam pressure and prevents leakage past the circum-
ferential edge of the plate. Springs are preferably arranged in the plate to bear
against the underside of the strip and assist in pressing it outwardly.
The jointed plates F consist each of a main portion F2 attached by the tapering
knuckle to the head A', and a wing F3 which is seated in the pocket of the piston
and connected with the main portion by a conical knuckle formed on the main
portion and entering a conical socket in the wing, see Figures 9 and 10. This
permits the wing of the plate to stand at a greater or less angle to the main portion

page_text: and enables the plate to adjust itself to the position of the pocket of the piston
without binding. The sides of the wing fit snugly against the sides of the pocket
but the sides of the main portion are contracted toward the knuckle f to afford the
main portion some play in the pocket. Each jointed plate is provided with a
packing strip G' which exiends over the circumferential bearing face of the main
portion and is provided with a detached cross bar g3 which is seated in the wing
and takes part in the oscillatory movement thereof on the knuckle f of the main
portion.
H, Figures 1, 5, 22 and 23, represents the wrist pin which is arranged centrally
on the spherical back of the piston and which projects into the steam chest and
enters a socket arranged eccentrically in the crank disc, so as to rotate with the
latter. His a collar arranged between the wrist pin and the piston and provided
with a suitable number of steam inlet openings h. The circular opening in the
crown of the spherical case is large enough to permit of the rotation of the wrist pin
and collar and is provided with a packing ring which is seated in a recess in the
opening and bears against the spherical back of the piston, Figures 5 and 6.
The wrist pin is surrounded by a sleeve I having an external spherical face and
the socket on the crank disc is provided with a bearing i, Figure 5, for the spherical
sleeve by placing the latter in the socket and pouring babbitt or other soft metal
around the same. This spherical connection permits the wrist pin and crank disc to
adjust themselves to any imperfections of workmanship or inaccuracies in the
arrangement of the parts.
The friction of the wrist pin in its socket can be materially reduced by using
the roller bearing represented in Figures 22 and 23. In this construction the
end of the wrist pin is reduced, as shown at j, and surrounded by a ring or
collar J which is secured to it. A thinner collar J is secured to the larger
portion of the wrist pin, both collars being of the same external diameter.
Rollers J are arranged between the outer faces of the collars and the inner
face of the ring J3 which is pressed into the spherical collar I. These rollers
are provided with reduced middle portions j2 and are held apart by a notched
carrying ring J which is arranged between the collars J and J' and receives
the reduced necks of the rollers in its notches. The centrifugal force generated
by the rotation of the wrist pin tends to throw the rollers toward the crank
disc and in order to reduce the friction occasioned by this pressure a row of
balls is arranged in an annular recess formed in the side of the rear colla: J
adjacent to the notched carrying ring, so that the latter bears against these
balls. The form of this notched ring is shown in Figure 4. This roller
bearing does not only reduce the friction by interposing the rollers between
the contact surfaces, but it also reduces the friction by reducing the one-
sided pressure against the wrist pin bearing which is much larger in a
wrist pin with a plain bearing, such as represented in Figure 1, because in such
a bearing the pin is pressed by the piston against one side of the bearing,
leaving a clearance on the other side of the pin into which the steam enters
which supplements by its pressure the one-sided pressure already applied to the
bearing by the piston. In the roller bearing the pin is practically exposed to
the steam pressure all around its circumference so that the steam pressure on
the wrist pin is practically balanced.
For the same reason it is desirable in many cases to employ a roller bearing for
the main bearing of the engine shaft which is adjacent to the steam chest and
exposed to steam pressure by leakage along the journal. Such a roller bearing is
represented in Figures 2, 3 and 4, in which K represents the rollers, kk the wear
rings applied to the shaft, the notched ring carrying the rollers, and ² the
wear ring secured to the bearing and surrounding the rollers.
L represents the cylindrical seat for the main valve arranged axially in the piston
and L are the curved steam ports of the piston extending from the sides of said
seat to the face of the piston and arranged between the pockets of the division
plates, as represented in Figures 5, 7 and 8.

page_text: M represents the cylindrical main valve open toward the exhaust end of the
engine and provided at its opposite end with a hollow stem m which connects
with the cylinder by a flaring hollow neck m'. The latter is provided with
the
openings m² Fig. 26 through which the steam enters from the hollow collar H',
cavity of which surrounds the neck m' and receives the steam through the
openings . m³ represents the steam induction port and m' the exhaust port formed
in the cylinder of the main valve on opposite sides thereof. In Figures 5, 7, 30
and 31, N represents the cylindrical cut-off valve which is arranged within the
main valve and provided with a stem n which extends through the hollow stem of
the main valve. The cut-off valve N is provided on one side with an exhaust port n¹
which is adjacent to and somewhat longer circumferentially than the exhaust
port m of the main valve and on the opposite side with a steam inlet port 2 which is
adjacent to and somewhat shorter circumferentially than the steam inlet port m³
of the main valve. The inlet and exhaust ports of the valves are separated by a
diagonal diaphragm n³ which is formed in the cut-off valve and which places the
exhaust ports in communication with the exhaust end of the main valve and the
steam ports in communication with the hollow neck. n is a rib arranged along
the rear or trailing edge of the steam inlet port 2 of the cut-off valve and projecting
outwardly into the steam inlet port m³ of the main valve with which latter the
cylindrical face of this rib is flush. The front edge of this rib performs the function
of cutting off the steam. The steam port is fully open, as represented in
Figure 7, when the rib rests against the rear edge of the steam port of the main
valve, and is closed to a greater or less extent by shifting the position of the
internal or cut-off valve, so as to cause the front edge of the rib n' to approach the
front edge of the steam port m³ of the main valve. This rib is secured to
the cut-off valve by screws or other suitable fastenings.
The main valve is rotated by a bifurcated carrier O which is secured to the
rear side of the crank disc, as represented in Figure 22, and rotates therewith.
Both valve stems project through the crank disc and the outer or hollow stem
has its sides flattened, as represented in Figures 26 and 28. The carrier plate
straddles the flattened portion of the hollow valve stem and compels the latter
to rotate with the crank disc. The inward pressure of the steam on the main
valve is received by this carrier plate which has the rear sides of its forked
branches rounded where they come in contact with the end portions of the
stem to permit these parts to adjust themselves to the angle of the main valve..
The inward pressure of the steam on the inner or cut-off valve is received by
a ball bearing, represented in Figures 22 and 26, which consists of a grooved
collar
P secured to the projecting end of the stem of the cut-off valve, a
of balls p seated in the groove of said collar and bearing against the end of
the hollow stem of the main valve and a ring p² whereby the balls are retained
in the groove. This ball bearing reduces the resistance of the cut-off valve
very materially and renders the valve very sensitive.
row
QQ, Figures 22, 24 and 25 represent the governor weights which are pivoted
to the rear side of the crank disc ou diametrically opposite sides of the engine
and a carrier
shaft and connected with the stem of the cut-off valve by links
plate R. The latter is secured to the projecting end of the valve stem and is
provided with two ears each having on its inner side a spherical socket in
which the spherical head of one of the links y is seated. The opposite
spherical heads of the links are seated in spherical sockets in the governor
weights. The governor weights swing in a plane at right angles to the engine
shaft, while the carrier plate R turns in an oblique plane, at right angles to
the valve stem. The spherical connection of the links with the governor
weights and the carrier plate permits these parts to move freely although
arranged at an angle to each other. T represents the springs which resist the
outward movement of the weights. These springs are secured to the peripheral
rim of the crank disc and bear with their free ends against adjustable bearing
pieces t secured to the outer sides of the weights. Each of these bearing pieces

page_text: is attached to the weight by a pivot bolts which is arranged parallel with the
pivot of the weight and which passes through approximately radial slots s' in
the weight, so that the bearing piece can be adjusted toward and from the
fulcrum of the weight by shifting the pivot bolt in these slots. Each bearing
piece is arranged in a recess in the outer side of the weight and can be adjusted
on its pivot bolt toward and from the spring by a set screw 2 which is screwed
into the weight and bears against the rear side of the bearing piece. The
latter is provided at its apex with rollers 3 by which it bears against the spring.
By adjusting the bearing piece in the weight the pressure which the spring
opposes to the outward movement of the weight can be nicely regulated.
The steam which has passed through the induction port of the main valve into
the piston presses against that part of the valve which is adjacent to the induction
port and crowds the valve against the opposite side of its seat. In order to
counteract this external pressure on the valve, the cylindrical surface of the
portion T¹ of the valve adjacent to the steam inlet is depressed or cut away on the
opposite side of the valve, as shown at t', Figures 26 and 29, so as to form a narrow
space between the surface of the valve and its seat into which the steam enters from
the steam chest. This steam applies external pressure to the valve in a contrary
direction to that which is applied to the induction side of the valve and whereby
the external pressure upon the valve is balanced completely or nearly so. In order
to prevent the steam from leaking along the valve to the ports of the piston, the
valve is provided with a packing ring 2, Figures 5 and 26, between the depressed
portion and the ports. The cut-off valve is provided with a similar depressed
portion t and a packing ring t for the same purpose.
In Figures 32 to 50, my inventions are illustrated as embodied in a reversible
engine. In these figures A represents the case, A¹ the head of the case, A² the
cylindrical extension of the case, B the steam chest and C the crank disc arranged
within the steam chest and formed with the engine shaft. e is a collar also formed
on the shaft within the steam chest and bearing against the adjacent end of the
main bearing to prevent as much as possible steam from leaking into the main
bearing. c is an annular groove formed in the shaft within the main bearing and
c² is the drain pipe communicating with the groove. Steam which leaks along the
shaft into the main bearing enters this groove and is carried off by the pipe c². It
is obvious that the annular groove may be formed in the bearing instead of the shaft.
D represents the piston, D' the division plates or abutments pivotally attached
to the head of the case and projecting across the steam space into pockets in the
piston and D2 the hollow follower pin or knuckle arranged in the cylindrical
extension A2 with its semi-spherical end seated in the correspondingly shaped
recess in the face of the piston.
E represents the cylindrical valve seat for the main valve and E' the steam
ports. F represents the cylindrical main valve having the tapering neck F' and
hollow stem F2.
G represents the hollow wrist pin projecting rearwardly from the middle of the
piston and connected with the latter by a hollow collar G' which surrounds the
tapering neck of the main valve. This collar is provided with openings g through
which the steam passes from the steam chest into the cavity of the collar, which
cavity surrounds the tapering neck of the valve stem and from which the steam
passes through openings g' in the neck into the cavity of the valve. The wrist pin
is surrounded by two cylindrical wear rings and an outer cap h² having
a spherical external face which is seated in the spherical socket formed in the
crank disc by pouring babbitt or other soft metal ³ into the socket in the crank
disc around the spherical cap. The outer portion of the latter extends inwardly to
the hollow stem of the main valve. The spherical cap is prevented from turning
about the valve stem by a pin 4 which is secured to the crank disc and projects
into a groove in the spherical cap. This groove is made long enough to permit
the cap to rock in its seat lengthwise of the engine in adjusting itself to the angle
of the valve stem.

page_text: I represents the cylindrical cut-off valve which is arranged within the cylindrical
main valve and fits snugly in the bore thereof. This cut-off valve is provided with
a hollow stem l' which extends forwardly beyond the valves and rearwardly
beyond the end of the hollow stem of the main valve.
J represents the reversing rod which is arranged in the bore of the hollow stem
This rod is
of the cut-off valve and extends rearwardly beyond said hollow stem.
provided with a longitudinal feather j which enters a groove in the stem of
the cut-off valve and compels the latter to turn with the rod, the groove being
longer than the feather to permit the rod to move lengthwise, while the cut-off
valve is incapable of lengthwise movement. This reversing rod is provided at its
front end with a spherical socket K which is guided in a cylindrical enlarge-
ment K¹ formed at the front end of the stem of the cut-off valve and arranged
within the hollow follower pin.
L* represents the shifting rod which is arranged axially in the cylindrical
extension of the head of the case and provided at its inner end with a spherical
socket. This socket is connected with the socket K at the front end of the
reversing rod by a link having spherical knuckles or heads at its ends, so that
the longitudinal movement of the shifting rod is transmitted by the link to the
reversing rod, while the link follows the rotative motion of the socket K which
rotates about the centre line of the case. The socket of the shifting rod is
guided in a cylinder which is arranged centrally in the hollow follower pin and
connected by radial arms (3 with the front end thereof, the spaces between the arms
permitting the exhaust steam to pass from the cavity of the pin into the
extension A² from which it escapes through the exhaust pipe .
m is a screw sleeve which is arranged in the head M of the extension A² and
bears against the outer end of the guide cylinder 12, so that the follower pin can be
adjusted inwardly by adjusting the screw sleeve, while the follower pin is free
to turn in the extension A2 in adjusting itself to the position of least resistance.
M' is the reversing lever which is pivoted to the lower part of the frame m' formed
on the head M and provided with a quadrant or segment m² on which the lever can
be secured in position by a clamping screw m³. The outer end of the shifting rod
is connected with the reversing lever so that the reversing rod is moved lengthwise
in the valves by shifting the lever.
N represents a carrier which is secured to the rear side of the crank disc,
as shown in Figure 32, or to the rear side of the spherical cap, as shown in
Figure 34, so as to rotate with the crank disc. When the carrier is secured to the
spherical cap it takes part in the adjustment of the latter in the spherical socket,
whereby binding is prevented. This carrier is provided with a bearing in which
the rear end of the reversing rod is guided and which is provided with one or more
radial pins or feathers n, each of which projects into a spiral groove n¹ formed in
the reversing rod. Two pins and two grooves arranged on diametrically opposite
sides, as shown, are preferably employed to equalize the strain, but one pin and one
groove may be used. Upon moving the reversing rod lengthwise by means of the
reversing lever, the rod is turned by the engagement of the spiral grooves with the
5 pins. The turning of the rod causes the turning of the cut-off valve by the feather
of the rod engaging in the groove of the cut-off valve.
O represents a carrier plate secured to the rear end of the stem of the
main valve and provided with two rearwardly projecting lugs 01 02 which are
arranged nearly diametrically opposite each other, as represented in Figure 39.
003 represents a lug or tooth formed on the base plate of the carrier N and adapted
to engage against the front or outer face of either of the lugs 01 02. The outer
faces of the lugs 01 02 may be cut down to the circular hub of the carrier plate
while the rear or inner faces of these lugs may be connected by a segmental
web O*. The tooth of the carrier plate resting against one of these lugs causes the
5 main valve to rotate in a certain direction and the piston to be actuated in the
corresponding direction. By turning the main valve so as to bring the other lug

page_text: against the tooth of the carrier plate the main valve is reversed and the direction
of movement of the piston is reversed.
P represents a collar which is secured to the rear end of the stem of the cut-off
valve and bears against the rear side of the carrier plate O of the main valve so as
to receive the inward thrust of the steam pressure on the cut-off valve.
Figs. 46 to 50 is a steam induction port and q¹ the exhaust port formed in
opposite sides of the main valve. r is the steam induction port and the exhaust
port of the cut-off valve arranged to register with the corresponding parts of the
main valve. R is the diagonal diaphragm formed lengthwise in the cut-off valve
around the stem thereof and separating the induction ports of both valves from the
exhaust ports of both valves, the induction cavity and ports communicating with
the hollow neck of the main valve and the exhaust ports and cavity with the open
end of the main valve, from which the exhaust steam passes into the hollow
follower pin. S is a movable cut-off segment which is arranged in the induction
ports of both valves and which rests against the rear or trailing edge of the
induction port of the cut-off valve or of both valves in either direction in which the
engine may run. This cut-off segment is composed of two plates, an outer plate S¹
having bevelled sides and fitting between the bevelled sides of the induction port
of the main valve, and an inner plate S² somewhat longer than the narrowest portion
of the outer plate and arranged in the induction port of the cut-off valve. Both
plates are secured together so as to form a segment having dovetail sides by which
the segment is attached to the valves but permitted to be shifted circumferentially
in the induction port of the main valve.
In the position of the parts represented in Figures 41 and 46, the crank disc and
the valves rotate in the direction of the arrows 1. The tooth 03 of the carrier rests
against the front or outer side of the lug O' of the main valve and causes the latter
to rotate with the crank disc. The pins of the carrier plate N engaging in the
grooves of the reversing rod, cause the latter to rotate with the main valve and
the feather on the reversing rod causes the cut-off valve to rotate with the
reversing rod. In this position of the cut-off valve, the induction ports q r of both
valves are wide open and the movable cut-off segment S rests against the rear edges
of the induction ports of both valves. In this position of the valves the reversing
rod is nearly in its rearmost position. By moving reversing rod forwardly, the
cut-off valve is turned to the right in Figure 46 in the direction in which it closes
the induction port of the main valve. In Figure 47, the induction port is shown
partly closed by the cut-off valve which has carried the movable cut-off segment
with it toward the front edge of the induction port. By continuing the forward
motion of the reversing rod, the cut-off valve and the segment finally close the
induction port of the main valve, as represented in Figure 48, thereby shutting off
the steam and stopping the engine. The cut-off segment now rests against the
front edge of the induction port. By continuing the forward movement of the
reversing rod still further, the cut-off segment now bearing against the main valve
causes the cut-off valve to carry the main valve around with it until the lug 0²
strikes against the tooth O³ of the carrier, as represented in Figure 44, in which
position the main valve is reversed, as represented in Figure 49, and the engine is
prepared to move in the opposite direction. The cut-off valve and segment still
close the induction port of the main valve and the reversing rod is in its foremost
position. The cut-off valve is now reversed and the induction port opened wide by
a partial backward movement of the reversing rod which is continued until
the opposite edge of the steam port of the cut-off valve rests against the cut-off*
segment, as represented in Figure 50.
If it is now desired to cut off, the reversing lever is further moved in the same
direction, so as to shift the cut-off valve and the cut-off segment and close the
induction port of the main valve to a greater or less extent. In order to reverse
the engine, therefore, the main valve is reversed by placing the reversing lever in its
opposite extreme position, the cut-off valve is next reversed and the induction port

page_text: f the main valve is opened wide by a short return movement of the reversing
ever, and the cut-off valve is shifted to partially close the induction port, if it is
lesired to cut off, by a further short return movement of the reversing lever.
The carrier plate O of the main valve is provided on its front side with an annular
roove in which are arranged balls t which bear against the spherical cap of the
vrist pin and reduce the friction between these parts. The collar P of the cut-off
alve is provided on its front side with a groove and a row of balls t¹ by which it
pears against the carrier plate of the main valve. These balls receive the end
thrust caused by the steam pressure against the valve and materially reduce the
friction between the parts.
My improved engine can be actuated by steam, compressed air or any other fluid
under pressure.
Having now particularly described and ascertained the nature of my said inven-
tion 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 case having the form of a spherical segment and the
similarly shaped piston filling the case partially, of a follower pin arranged in the
case and bearing centrally against the piston, and an adjusting screw having a
swiveling connection with the follower pin, substantially as set forth.
2. The combination with the case having the form of a spherical segment and the
similarly shaped piston filling the case partially, of a division plate or abutment
consisting of a main portion having a pivotal or rocking connection with the case,
and a wing connected with the main portion by a flexible joint and entering a pocket
in the piston substantially as set forth.
3. The combination with the case having the form of a spherical segment and
the similarly shaped piston filling the case partially, of a rigid division plate having
a pivotal or rocking connection with the case, and jointed division plates composed
of a main part and a wing connected by a flexible joint, substantially as set forth.
4. The combination with the spherical case and the spherical piston, of a division
plate provided with a conical knuckle seated in a similarly shaped recess in the case,
substantially as set forth.
5. The combination with the spherical case and the spherical piston, of a division
plate capable of radial movement in the case, and a spring whereby the plate is
pressed inwardly, substantially as set forth.
6. The combination with the case having the form of a spherical segment and
provided with a circular opening in its crown, of a steam chest attached to the case
outside of said opening, a spherical piston provided with a wrist pin rotating in said
opening, a crank disc arranged in the steam chest and connected with the wrist pin.
a valve whereby the flow of steam from the steam chest to the case is controlled,
and an annular packing strip loosely seated in the circular opening of the case and
pressed by the steam pressure in the steam chest against the back of the piston,
substantially as set forth.
7. The combination with the spherical case having an opening in its crown and a
steam chest attached to the case outside of said opening, of a wrist pin attached to
the piston and projecting through said opening into the steam chest, a crank disc
arranged in the steam chest and provided with a socket for the wrist pin, and rollers
interposed between the wrist pin and its socket, whereby the steam pressure is
equalized around the wrist pin, substantially as set forth.
8. The combination with the spherical case, of a spherical piston provided with a
wrist pin, a crank disc provided with a socket for the wrist pin, interposed rollers
provided with reduced middle portions, and a notched ring carrying said rollers,
substantially as set forth.
9. The combination with the spherical case, of a spherical piston provided with
a wrist pin, a series of connected rollers arranged between the wrist pin and its
socket, and a ball bearing whereby the outward thrust of the rollers is received,
substantially as set forth.
B

page_text: 10. The combination with the spherical case, of a spherical piston provided with
a hollow wrist pir, a valve seated in the piston and provided with a stem extending
through the wrist pin, and a carrier attached to the crank disc and engaging with
the valve stem, substantially as set forth.
11. The combination with the spherical case, of a spherical piston provided with
a hollow wrist pin which is connected with the piston by a hollow collar having steam
inlet openings, a hollow valve arranged within the piston and having a hollow neck
and stem arranged within the collar and wrist pin, the neck of the valve being
provided with steam inlet openings, substantially as set forth.
12. The combination with the spherical case, the spherical piston provided with
a hollow wrist pin and the crank disc, of a main valve seated in the piston and
provided with a hollow stem extending through the wrist pin, a carrier attached
to the crank disc and rotating the main valve, a cut-off valve arranged in the main
valve and provided with a stem extending through the stem of the main valve, and
a governor mechanism attached to the crank disc and connected with the stem of the
cut-off valve, substantially as set forth.
13. The combination with the spherical case and the spherical piston, of a hollow
main valve, a cut-off valve arranged in the main valve, and a ball bearing interposed
between the stem of the cut-off valve and that of the main valve, substantially as
set forth.
14. The combination with the cut-off valve and the crank disc, of governor
weights pivoted to the crank disc, springs secured to the crank disc, and adjustable
bearing pieces attached to the weights and bearing against the springs, substantially
as set forth.
15. The combination with the spherical case, the spherical piston arranged
obliquely in the case, and the crank disc, of governor weights pivoted to the crank
disc, a cut-off valve arranged centrally in the piston, a carrier secured to the stem
of the cut-off valve, and links having spherical heads which connect the weights
with said carrier, substantially as set forth.
16. The combination with the spherical case and the steam chest attached thereto,
of a main bearing opening into the steam chest, a shaft and crank disc arranged
in the steam chest, and rollers interposed between the shaft and the main bearing,
whereby the steam pressure on the shaft is balanced, substantially as set forth.
17. The combination with the case having the form of a spherical segment and
the similarly shaped piston filling the case partially, of a reversible main valve
arranged in the piston and moving therewith, and a reversible cut-off valve arranged
in the main valve, substantially as set forth.
18. The combination with the case having the form of a spherical segment and
the similarly shaped piston filling the case partially, of a reversing rod capable of
rotative movement, a reversible cut-off valve which is rotated by said rod, and a
reversible main valve which is arranged in said piston and shifted by the cut-off
valve, substantially as set forth.
19. The combination with the case, the piston and the crank disc, of a valve
arranged in the piston, and capable of rotative movement, but held against
longitudinal movement, a reversing rod capable of longitudinal movement in said
valve and rotary movement with said valve and provided with a spiral groove, and
a carrier attached to the crank disc and provided with a projection which enters said
groove, substantially as set forth.
20. The combination with the spherical case and piston, of a main valve arranged
in the piston, a cut-off valve, arranged in the main valve and provided with a hollow
stem having a guide at its front end, a reversing rod arranged in said hollow stem
and provided at its front end with a spherical socket which moves in said guide, a
shifting rod provided with a spherical socket, and a link having spherical knuckles
and connecting said sockets, substantially as set forth.
21. The combination with the spherical case and piston, of a cylindrical extension
arranged on the head of said case, a hollow follower pin arranged in said extension
and provided with a cylindrical guide, a spherical socket arranged in said guide and

page_text: connected with a shifting rod, a reversible valve arranged in the piston, a reversing
rod arranged in said valve and provided with a spherical socket, and a link having
spherical knuckles and connecting said sockets, substantially as set forth.
22. The combination with the spherical case, the piston and the crank disc, of a
carrier revolving with the disc and provided with a projection, and a reversible
main valve arranged in the piston and provided with two projections, either of
which can be brought in contact with the carrier, substantially as set forth.
23. The combination with the spherical case, the piston and the crank disc, of a
carrier attached to the disc and provided with a projection, a reversible main valve
provided with two projections, either of which can be brought in contact with the
projection of the carrier, and a reversible cut-off valve provided with a movable
segment whereby the main valve is moved, substantially as set forth.
24. The combination with the main valve and the cut-off valve, both provided
with induction ports, of a detached cut-off segment arranged in the induction ports,
substantially as set forth.
25. The combination with the case having the form of a spherical segment, the
similarly shaped piston filling the case partially and provided with a wrist pin, and
the crank disc provided with a seat for the wrist pin, of a main valve arranged in
the piston and having a stem which extends through the wrist pin, and a ball
bearing which is interposed between said valve stem and its support in the crank
disc and whereby the inward thrust of the main valve is taken up, substantially as
set forth.
Dated this 18th dox of August 1891
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C., Agents for the Applicant.