IMPROVEMENTS IN ROTARY ENGINES
Year: 1882

page_text: LETTERS PATENT to Herbert John Haddan, of Kensington, Middlesex for an
invention of IMPROVEMENTS IN ROTARY ENGINES A communication to him
from abroad by Leander Joseph Wing, of Washington, District of Columbia,
United States of America
L
PROVISIONAL SPECIFICATION left by the said Herbert John Haddan at
the Office of the Commissioners of Patents on the 23rd May 1882.
دل 1
$
HERBERT JOHN HADDAN, of Kensington, Middlesex, IMPROVEMENTS IN ROTARY
ENGINES, a communication to me from abroad by Leander Joseph Wing, of
Washington, District of Columbia, United States of America,
The invention consists in the combination with a rotary piston disk of a rotary
abutment 'disk' arranged at right angles to the rotary piston disk and suitable
mechanism for imparting a continuous rotary motion thereto and having the
periphery of said abutment disk arranged to snugly fit against the periphery of the
piston disk
Also in the combination with a rotary piston disk having a concave periphery
of a rotary disc abutment arranged at right angles to the piston disk and provided
with a concave periphery, and suitable mechanism for imparting a continuous
rotary motion thereto.
F
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Also in the combination with a self-adjusting revolving piston and tapered piston
extensions of a rotary disk abutment arranged to revolve at right angles to the line
of movement of said piston.
Also in the combination with the cylinder provided with an annular bore made
circular in cross section of a rotary disk abutment arranged to rotate at right
angles to the annular bore, and to open and close the same and with suitable
nechanism for transmitting a continuous rotary motion thereto.
Also in the combination with a cylinder and revolving piston and piston disk of
a rotary disk abutment, arranged at right angles to the revolving piston, and
cylinder extensions provided with self adjusting packing for packing the sides of
the abutment and piston disk.

page_text: Also in the combination with a rotary piston disk provided with piston
extensions and self adjustable piston located between the adjacent ends of said
extensions, of a rotary disk abutment, arranged at right angles to the rotary piston,
and provided with an irregularly curved cut away portion for the passage of said
piston and piston extensions.
Also in the combination with a revolving piston of a rotary disk abutment
mounted on a shaft and arranged at right angles to the revolving piston and
devices for imparting adjustment to said shaft and rotary disk abutment.
Also in the combination with a rotary piston disk of a piston connected therewith
said piston being provided with an expansible packing ring constructed with a
projection that is split by a vertical and horizontal wall.
Also in the combination with a rotary piston disk of a piston a weight lever and
connecting links for counter balancing the piston.
Also in the combination with a rotating piston disk and a piston provided with
expansible rings of devices connected with the inner expansible ring, for counter
balancing the action of centrifugal force on the piston.
Also in the combination with the packing rings of the cylinder extensions of
devices for regulating the inward pressure on said packing rings.
Also in a rotary abutment disk cut away on one side for the passage of the
piston and cored out on its opposite side to balance the disk
Also in a cylinder for rotary engines consisting of two sections having one or
more abutment recesses located at right angles to the bore and flanges between
the hub and abutment recesses for the insertion of bolts for fastening the sections
together.
Also in a cylinder for rotary engines constructed in sections and provided with
an annular bore for the piston and intervening space for the piston disk the end of
the section being grooved around the bore, said groove extending to the opposite
sides of the space for the piston disk and provided with a series of pockets for the
reception of springs for keeping the packing rings pressed outwardly against the
revolving abutment.
Also in the combination with a rotary valve of a rotary governor valve seated
on the rotary valve the adjacent faces of the two valves being recessed or grooved
to provide an intervening steam space and suitable devices for automatically
actuating the governor valve.
Also in the combination with a steam balanced rotary valve of a steam, balanced
cut off valve serving as seat for the rotary valve, and a steam balanced governor
valve seated on the upper face of the rotary valve.
Also in the combination with the rotary valve provided with through ports of
the cut off valve constructed with ports, and with steam cavities or recesses, on
opposite sides of said ports, the rotary valve being balanced and steam cut off
at any point of its rotation.
Also in the combination with the rotary valve provided with a number of holes
for the passage of steam through the valve, and an annular groove on the opposite
side with which said holes communicate, of the rotary governor valve, having a
grooved or recessed portion formed therein that registeres with said annular
groove.

page_text: SPECIFICATION in pursuance of the conditions of the Letters Patent filed
by the said Herbert John Haddan in the Great Seal Patent Office on the
23rd November 1882.
HERBERT JOHN HADDAN, of Kensington, Middlesex "IMPROVEMENTS IN
ROTARY ENGINES," a communication to me from abroad by Leander Joseph Wing, of
Washington, District of Columbia, United States of America
In the accompanying drawings which illustrate this invention Fig 1 is a front
view of an improved engine. Fig: 2 Is an end view of the same the fly wheel
being shown in dotted lines. Fig: 3. Is a view in side elevation of the inner half
of the annular cylinder showing the ports the cylinder extensions in Section and
the piston disk, piston extensions and centrifugal balance in dotted lines
Fig: 4 Is a perspective view of the inside of the annular cylinder showing the
piston disc and the piston extensions passing through the cylinder extensions and
the abutment which is shewn in proper position
Fig: 5 Is a view of the piston disc with its extensions, the piston being in
position for operation, and the cone in the hub of the same the centrifugal balance
being shown in dotted lines-Fig: 6-Is a view in side elevation of the piston ring.
Fig: 7. Is a side view of the piston. Fig 8 Is the cap plate of the piston.
Fig 9, Is a side view of the shell of the piston. Fig: 10 Shows the rings inserted
in the piston shell.-Fig 11. Is a vertical section taken through the cylinder and
rotary abutment. Fig: 12. Is a view in outline of the parts shown in Fig: 11
with the abutment in position to form a cylinder head, Fig: 13. Represents a
packing Ring for the Cylinder Extension showing the Springs connected therewith
Fig 14. Is a view in perspective of one of the cylinder extensions-Fig: 15. Is a
cross section of Fig: 14 on a line X X. Fig: 16. Is an enlarged view of the lower
left hand portion of Fig 14 showing the appliance for packing the piston disc in
the Cylinder extensions. Fig: 17. Is a view in cross section of the Cylinder with
the Steam jacket applied to the same-
-Fig 18. Is a rear view in outline showing
the mitre gears by which the abutement is operated. Fig: 19. Is a diminished
view of the outside showing the application of the Steam Jacket thereto.
Fig 20 Is an enlarged view of the adjustable bearings for the abutment shaft.
Fig: 21 Is a view in vertical section of the thrust bearings for the abutment
shaft with the check nut also the set screws, discs and shaft in position-Fig: 22.
Is a transverse section taken through the block L'-Fig: 23. Is a view in side
élevation of said block. Fig: 24. Is an end view of a modified form of construction
of engines embodying this invention-Fig: 25. Is a side elevation of another
engine embodying this invention a portion of the Cylinder being broken away to
illustrate its interior construction. Fig: 26. Is a plan view of the inner sides of
one section of a modified construction of Cylinder embracing the features of both
Figs: 24 and 25. Fig: 27. Is a sectional view of the same. Fig: 28. Is a view
in perspective of the valve Cylinder and the gearing for actuating the valves of
this engine. Fig: 29. Is a longitudinal section taken through the valve cylinder,
Fig: 30. Is an end view of the valve cylinder with the outer head removed-
Fig 31. Is a detached view of the gearing for adjusting the position of the
govenor valve. Fig: 32. Is a rear plan view of the inner head of the valve
cylinder. Fig: 33. Is a similar view of the front surface of the inner head of the
cylinder. Fig: 34. Is a view of the front face of the rotary valve. Fig: 35. Is a
transverse sectional view of the same-Fig 36. Is a view of the rear face of the
rotary valve. Fig: 37. Is a view of the front face of the cut off valve-Fig: 38.
Is a transverse Sectional view of the same.-Fig: 39. Is a view of the rear face of
the cut off valve. Fig: 40. Is a detached view of the worm and worm gear for

page_text: actuating the Govenor valve. Fig: 41. Is a front plan view of the Govenor
valve Fig: 42. Is a rear plan view of the govenor valve. A represents the bed
of the Engine having two outwardly projecting flanges A', A', to the outer side of
which are secured the inner Sections E E¹ of the annular Cylinder F by means
of bolts passing through the ears E2 E2 and flanges A', A¹ serving to secure them
firmly together. The bed A is also provided with stays or braces A2 A2 to impart
additional strength and stiffness thereto. The standards B. located at opposite ends of
the bed A. may be cast integral with the bed A or secured thereto by bolts as shown
in Figs 1 and 2. In the upper end of each standard B is formed an 'elongeted seat B¹
within which are placed the wedges B². B². with set screws c c engaging with the
thick end of each wedge as shewn in Fig: 2-Resting upon the flat surface of the
upper wedge is the foot B³. of the main bearing C which foot is adapted to fit
in the slot B5 at either end of the elongated seat B¹-A movement either forward
or backward of the wedges B². B². by means of the set screw's C. C. raises or lowers
the foot B³. and so adjusts the main bearing C, to compensate for any wear thereof.
After the bearings C have been adjusted to the proper 'height the feet B³ are
secured in place by means of the top bolts B. B. which pass through elongated
slots in the wedges B2 B2 and enter screw threaded holes in the elongated seat B¹
E and E are the outer and inner sections of the annular Cylinder F-which two
Sections are firmly secured to each other by means of' bolts passing through the
flange of Section E into the flange of section E¹³, the inner faces of which flanges
are fitted to form a Steam tight joint when thus 'firmly bolted' together." On the
ópposite sides of the section E' are formed the ears E². E. to secure the same to
the flanges A¹ A¹ and joined to the upper end of these ears E2 E2 are the
projections E3 E3 to which are secured the main and thrust bearings of the shaft N'
of the abutment disk N.-In the inner surface of the Sections E and E¹ is formed
the annular cylinder F by means of a semi-circular groove in each section which
extends entirely around the Sections, so that when the two sections E and E' aré
secured together an annular cylinder F is formed therein, the bore of the Cylinders
being shown in Figs: 11 and 12-In the upper part of the annular Cylinder F is a
slot L extending somewhat below the bore of the Annular Cylinder F and upwards
entirely through the annular Cylinder F, and flanges which slot is sufficiently
wide to allow the two cylinder extensions F¹ F¹ to be fitted into it on either side
sufficient space being provided between the Cylinder extensions F. F' to allow the
abutment disc N to freely revolve between the same as shown in Fig: 4. In the
centre of the Sections E and E' is a hole or opening shewn in Fig: 3 in which
the hub K; of the piston disc I is made to revolve and on the outside it forms a
hub to which the stuffing box E is bolted-Between the two Sections E and E¹
a sufficient space is formed to allow the piston disc I to freely revolve therein as
shown in Fig 11. On each section E and E¹ of the Annular Cylinder F just
inside the bore and upon the flat surface which comes in contact with the piston
disc I when in position is a groove H extending entirely around the Sections E
and E¹ of sufficient width and depth to contain a ring H2 tightly fitted therein
with tempered steel coil springs H behind the ring H2 which by engaging against
the side of the piston disc I near its periphery prevents the escape of steam to the
hub K of the piston dise I and also compensates for wear. At the bottom of the
section E¹ of the annular Cylinder F is an opening F5 see Fig: 11. to which is
attached a cock (not shown) to relieve the Annular Cylinder F of water of
condensation when required-The Cylinder extensions F F¹ Figs. 3. 14. 15. 16 are
fitted within the slot Ĺ of the annular Cylinder F so as to be steam tight and are
secured in proper position by bolts a aa as shown in Fig. 1, in which position
they are bored out at the same time the Cylinder F is bored and constitutes a
continuation or Segment of the Cylinder and this office is to allow of the cutting
of a groove F* in their inner surface just around the bore of the annular Cylinder F,
into which groove F* is nicely fitted a ring F2 Fig: 13-Beneath which ring F are
set in the groove F* of the Sections F1 F1 tempered steel coil springs F3 to keep
the rings F constantly forced against the side surfaces of the abutment disc N,

page_text: 1
and so keep it steam tight while performing the office of a revolving or movable
cylinder head. The bottom of the bore of the Cylinder extensions F¹. F¹. is cut
away and within such cut away portion is snugly fitted the sides of the piston
disc I-On either side of this cut away section is a slot F in which is fitted steam
tights the metal packing pieces F with springs behind them (said Springs not
shown) which, nietal pieces F engage against the sides of the revolving piston
disc I and pack it, in fact they are extensions of the packing rings H² H²
set in sections E and E' of the annular Cylinder F and perform the same office
The projections E³, Es an purposely attached to the flanges of Section E' of the
annular Cylinder F to facilitate the removal of section E when desired and allow
the Section E to remain in its usual position. On the outside of section E¹
surrounding the outside openings from ports X and W is a flange E³ to which the
valves for ingress and egress of steam are secured. On the outside of Sections E
and E' surrounding on three sides the slot L, sufficient metal surface, is allowed to
give the necessary strength to the cylinder at that point Also to allow for firmly
securing thereto the pockets M¹ M', cap M, and stuffing boxes S. The piston disc I
consists of a disc of sufficient thickness to insure the strength requisite to carry
the piston, the diameter of which disc being just equal to the diameter of the
packing Rings H2 in Sections E and E' of the annular cylinder F. In the centre
of the disc I and on either side is a hub K of sufficient size to allow the main
shaft D to pass through it and yet allow sufficient remaining metal in it to secure
the necessary strength-Each end of the opening in the hub K. is made funnel
shape. The main shaft D is inserted through the hub. In each end of the hub K.
is placed a Cone K'. which is bored through its centre to allow the main shaft D
and feather thereon for which a spline is cut, to pass through it easily.-The cone
is split throughout its length so that when two cones K¹ K¹ are drawn into the
hub K. by means of the bolts shown in Fig. 11 they are made to clasp tightly
around the shaft and feather and thus a strong and durable yet easily detachable
connection is made between the piston disc I and the main shaft D. The periphery
of the piston disc I is curved to suit the circumferential curve of the abutment
disc N which revolves across it See Figs: 4. 11. and 12-On, the outer edge of, the
piston disc I is formed two segmental extensions 13 13 between which is the slot I
in which the piston G is carried, a smaller slot I on one side of the slot I¹ receives
the projection G of the piston G and thus secures it rigidly against any radial
movement in the slot -The length of the Segmental extensions 12, 13, is in the
present case about one fourth of the circumference of the Cylinder but they may
be longer or shorter according to the diameter of the abutment disk N... These
extensions are a little smaller than the bore of the annular cylinder and are cored
out in the centre leaving only metal enough to take the steam pressure and are cut
away from the slot I' to the end of each to adapt them to the movement of the
cut away Section in the abutment disk N while the piston G is passing through it.
See Fig 4. The function of these piston extensions I² and I³ is to fill as far as
possible with hollow metal that space in the cylinder intervening between the port
of ingress, and the abutment, disc N just at the time when steam is admitted to the
annular cylinder F, and hence they serve to reduce the 'clearance, just the bulk of
one of these extensions in each cylinder at each revolution of the piston G-On
the side of the piston disc I between the hub K. and the slot I' is an opening b in
which is placed a lever J. with a movable fulcrum d in its centre, and a rod e.
attached to one end, the opposite end of this rod being attached to the ring G³ of
the piston. This device as a whole may be called a centrifugal balance and is
designed to counteract or Counter balance the effect of centrifugal force applied to
the piston ring G, 2 when the piston G is revolving rapidly about the annular
cylinder F It will be seen by the foregoing description that the sides or frame of
the piston is rigidly fixed between the piston extensions 12. Is the rings G² and G³
alone being flexible or movable radially, hence one rod e attached to the lever J, is
secured to the inner ring, G³ of the piston G through an opening sufficiently large
in the bottom or projected part of the outer ring G2, and the rod e¹ attached to

page_text: the other end of the lever J, is attached to a ball J¹ of metal located in the cavity
of the piston extension 12-The weight of which ball J¹ is equal to the weight of
the piston rings G2 and G³ hence the action of the centrifugal force on the ball J¹
is just equal to its force upon the rings G2 and G³ and the movable fulcrum d
allows of the proper adjustment to overcome any friction of the rings G2 and G³
between the two heads G¹ and h of the piston G-To adjust this an opening is left
in the Section E of Annular Cylinder F which is covered by a Cap f bolted on and
removable at will shown in dotted lines in Fig: 2-The ball J' is suspended within
the cavity of the projection I2 by a flat steel spring g the ends of which are
supported by hooks g'-The ends of the spring 9 are formed with elongated
openings to allow of a radially flexible movement of the ball J' and yet cause it to
be carried with the piston disc in either direction-The piston G is constructed
with a plate h which is circular except for about one eighth of its circumference
which projects outwardly for a purpose hereinafter stated. On the back of this
plate is a projection G4 the use of which has already been stated. Upon this plate
are five projections or bosses G³ to which is bolted the corresponding plate G'.-
This constitutes the frame of the piston G, the plates G¹ and h forming what is
usually known as piston heads-The piston G is further provided with two rings
one G2 being the outer ring which is formed to fit the peculiar curve of the annular
cylinder F being concave to fit the inner surface and convex to fit the outer surface
of the annular cylinder F-It will be remembered that the packing rings H2
in sections E and E' of the annular cylinder F were set in somewhat from the bore
of the cylinder see Figs 11 and 12 to secure sufficient strength of metal between
the groove H. and the bore of the annular Cylinder F-In order to compensate for
the wear between the disc I and that part of the annular Cylinder F which is
situated between the bore and the groove H the outer packing ring G² is extended
down into the piston disc I far enough so that the projected Section shall cover
such intervening space and as the ring G2 is split at the bottom it is made to
compensate for wear not only around the bore of the Cylinder F but also so far
down into the space formed for the admission of the piston disc I as is necessary
to secure a steam tight and wearing fit. For this purpose the outer piston ring G
is cast of greater diameter than the bore of the cylinder and in the projection
thereof a groove is planed out of it from opposite sides to form the cut shewn in
Fig 10 it is then compressed and its outer and inner surfaces turned as required so
that when it is put in its proper position it must be compressed to be put into the
Cylinder and will expand in the projection to pack the aforesaid intervening space.
The inner ring G³ is of greater outer diameter than the inner diameter of ring G²
and is cut and then compressed and the outside turned to fit the inside diameter
of ring G2, the ring G³ is then turned eccentric on the inside, so that when it is
placed on the inside of ring G2 the expansion of both rings will secure a uniform
expansion of the entire circle of the outer ring. Should the bore of the Cylinder F
wear unequally this can be obviated by varying the shape of the inner ring-This
device in connection with the centrifugal balance before described causes the
annular cylinder F to wear in a circle in its circumferential contact with the
piston G. The peculiar form of the cut i in the projected Section of the ring G³
prevents the escape of any steam through it, should the piston G for any reason
become filled with steain, since the edges of the ring G2 form a ground or steam
tight joint between the piston heads G' and h, which heads are provided with
extensions like that in ring G2-In order to secure a proper speed of the piston
and not necessitate too large a circle of the Annular Cylinder F the abutment
should have a continuous movement simultaneous with the piston, for this reason
I use a revolving abutment thus avoiding any reciprocating motion which latter
greatly retards the speed and is more liable to become impaired in use-This
Abutment N consists of a disc whose diameter is three times or more the diameter
of the bore of the annular cylinder F, A shaft N' passes through the hub of the
disc N to which it is firmly secured-The disc N is of sufficient thickness to secure
the necessary strength of metal so that it will not spring or break under the

page_text: A
pressure of steam-A section is cut away from the disc N as shewn in Figs 4. 11
and 12. sufficiently large to allow the piston G to pass while the disc N is in
motion and not come in contact with it-Opposite the cut away section the disc N
is cored out sufficiently to offset the metal cut away, so it will be balanced in
itself and capable of great speed thereby. The periphery of the disc N is curved
to match the circumference of the piston disc I across which it revolves-As
both discs move together the movement is a spiral or diagonal movement and well
adapted to form a nice surface on the line of contact between the two. The shaft
N' rests in the adjustable bearings O. O. which bearings are secured by bolts to
the brackets E Es of the projections ES E³ of Section E¹ of the annular cylinder F
see Figs 1 and 2. The bearings 0. O. like the main shaft bearings C, C, rest upon
wedges which furnish ample means for a fine adjustment see fig: 1 by means of
set screws o' and bolts o². The ends of the shaft N' rest in the thrust bearings P, P,
which bearings are secured to the projections E³ Es by bolts which hold them in
the slots to which their lower projection is nicely fitted and allow of any vertical
adjustment desired. Thus it will be seen that the abutment disc N can be very
nicely adjusted in its contact with the piston disc I by the use of the set screw o
and bolts o2 see Fig: 1 The bearing O is shewn in detail in Fig: 20. They may be
of any desired length and may be bubbitted or made solid as prefered-The thrust
bearings P P are shewn in detail in Fig 21, the shaft N' is made to project partly
into the thrust bearing P its end pressing against the outer face of one of three
(more or less) hardened steel or case hardened iron discs P2 of the diameter of the
shaft N' or less, These discs are provided with a slot (not shown) in them to aid in
lubrication and they in turn rest against the face of a thrust bearing disc P³ having
a long screw projecting from its centre which is fitted into the rear part of the
bearing P and is adjustable by means of a wrench applied to the outer square end
of the same when the check nut P is removed, and the set screw P¹ is loosed.
cap R covers that part of the bearing P in which the end of the shaft N¹ and the
discs P2 are placed. By this means the abutment disc N is very finely adjusted
between the rings F3 of the cylinder extensions F' F' this device also provides for
any wear between the end of the shaft N' and the discs P or thrust bearing disc Ps
In the rear as seen in Figure 18 there is a mitre gear secured to the shaft N'
which revolves the abutment disc N, which gear is made to revolve by means of
similar gears on the shafts Q and Q¹ which connect with the like gear on the main
shaft D so that the abutment disc N is made to revolve simultaneously with the
main shaft D and as both piston and abutment have a continuous movement any
desired speed of piston or of the main shaft is attainable and as the movements are
steady, and no unequal strain is placed on any one part of the engine it is not
liable to get out of order. By enlarging the circle of the annular cylinder a greater
leverage is obtained between the piston and main shaft, hence the capacity of the
engine is increased at, will. The shaft N' is provided with stuffing boxes S S which
are secured by bolts to the top of the annular cylinder F and the bottom of the
cap M so as to allow of the shaft N' being lowered when desired to take up for any
wear between the two discs I and N. To avoid any tendency of the rings F° F²
being displaced by the action of the springs F3 during the passage of the cut away
section of the abutment discs N a device shewn in Figs 22 and 23 is introduced
into the slot L between the two cylinder extensions F1 F1 which device consists of
a block L of iron or other metal adapted to fill the space before mentioned see L¹
figure 11. near the bottom of which block is a groove L² extending entirely through
the block for about one half the length of the block and from thence to the outer
end the bottom of the groove is wedge shaped coming nearly to the surface at the
outer end fastened to the wide end of the block L' by screws is a spring L³
extending in the groove L² the full length of the block L so that its extreme inner
ends shall engage with that part of the ring F2 F2 extending below the line at
which the periphery of the abutment disc N passes the ring F2 see figure 16. The
screws L L passing through the movable wedge shape pieces L³ L' adjust
the rings F2 F2 so that the cut away section of the abutment disc N shall

page_text: closely shear by the rings F2 F2 and so avoid any concussion which might
otherwise occur. In Figures 17 and, 19. is. shewn the manner in which a
steam jacket can be very easily applied to the cylinder when that method of
protection is preferred to a covering of the cylinder by some non conducting
material so much in general use, A simpler form of centrifugal balance may
be used than that shewn in Figure 5 where only one uniform speed of piston
is required as in the case of stationary engines and may be described as follows:
a wide steel spring in shape like the letter C with a hole in the back, through
which passes the rod e¹ Figure 5 with check nuts thereon engaging against the
outside of the spring, which spring being placed in the opening J, is made to act
with greater or less force upon the rod e¹ and piston rings G and G³ by means of
the.check nuts which are adjustable through the opening in the cylinder shewn in
dotted lines in the cut section in the lower portion of bearing C Figure 2. All the
moving parts of the engine are finely adjustable and full provision is made to
compensate for wear. Although two cylinders are shewn in Figure 1 but one
cylinder is necessary in cases where a fly wheel can be used to carry the piston
over centres as in the case of stationary engines.. Besides the bearings C for the
main shaft shown in Figures 1 and 2 there are two other adjustable bearings
between the two cylinders in Figure 1 (said bearings not being shewn) In
Figure 24 is shewn a modified form of the engine in which one cylinder is used
instead of two and two abutments are used and preferably situated on opposite
sides of the cylinder F. The two ports W. and X sustain the same relation to the
abutment in the matter of position as in the double engine shewn and there are
two other ports Y and Z situated in like position. By this form of construction
greater simplicity is attained, the engine is made more compact, and the cost of
building is reduced and while it secures the same efficiency it saves the friction on
one piston. To understand its operation let it be borne in mind that the left
hand abutment N' has just closed and steam is being admitted at port W driving
the piston (which has passed that port) from left to right or towards port X, which
port remains open until the abutment N5 begins to open when the port X will close
and remain closed until the piston has passed the abutment N³, and just, at the
time the abutment N5 closes behind the moving piston, and while the space
between said abutment and the piston is filled with part of the steam admitted at
port W, the valve at port X opens to exhaust the steam contained in the cylinder F,
which steam has just forced the piston G past the abutment N³. At the same
time the valve at port Z opens to admit live steam into the space behind the
piston already filled with attenuated steam which newly admitted steam in turn
forces the piston along the cylinder F in the same direction as before past the
lately open but now closed port Y and the lately closed but now open abutment N*
which immediately closes behind the piston G when the same process of simul-
taneously admitting steam in front of the abutment and exhausting it behind takes
place, hence steam is admitted twice into the cylinder at each revolution and by
this means a constant steam pressure is maintained against the piston during the
entire revolution and without interfering with the continuous movement by the
piston in one direction and also without detriment to the facility of the engine for
automatic cut off and expansion of steam-All of the features of the annular
cylinder, the piston, the piston disc, the abutment, the centrifugal balance, the
cylinder extensions, the adjustable bearings, the packing rings, and devices for
compensating for wear in the double engine shewn complete in Figure 1 apply to
this modified form of construction which in reality simply eliminates one cylinder
and one piston and their necessary concomittants. Figures 25, 26 and 27 show
another modification in the form of the annular cylinder F. The abutment N
mounted on the shaft N¹ is caused to rotate within the slot L formed in the upper
section of the two half cylinders shewn in Figure 25 which are joined together on
a line with the abutment the two halves of the cylinder are each constructed with
flanges Es through which are inserted the bolts E by which the sections of the
cylinder are securely fastened together, each half or section of the cylinder is

page_text: provided with four lugs or projections Es cast intregal therewith, these lugs or
projections are located on opposite sides of each end of the hub portion of the
cylinder sections, and are arranged to project outwardly from. the division line
of the two sections, so that the lugs or projections on one section will overlap and
engage the hub portions of the opposite section, and so that the lugs of one section
will engage those of the opposite section.
.75
Thus it will be observed that this construction of parts prevents any lateral or
rotary displacement of the hub sections, as the lugs serve to securely lock the two
sections of the cylinder against any independent movement. In order that both
sections of the Cylinder may be cast from a single pattern and further to allow
them to be reversed in their position if desired, the lugs or projections E5 on one
Cylinder are arranged to fit against the lower and plain faces of the lugs E of the
other section of the Cylinder. Or in other words the lugs on each Cylinder
section are situated either all above or below the line of contact with the lugs on
the opposite section when the two sections are secured together and thus the two
sections are rendered interchangable-This feature of construction is valuable and
important for the following among other reasons-First in finishing the Cylinder,
the two sections are secured together by bolts and the lugs or projections, and then
they are bored out by a tool inserted within the hub and after the Cylinder is
bored the packing grooves and adjacent surfaces finished, the tool may be with-
drawn and the Cylinder set up for use with its piston packing rings &c. When
the sections of the Cylinder are put together they will always be in proper align-
ment and thus the wear of the piston and friction, of the parts will be reduced to
the minimum. This form or manner of dividing the Cylinder furnishes proper
facilities for finishing the packing grooves F surrounding the bore of the Cylinder,
on each side of the abutment chamber or slot L and also for drilling the holes for
the tempered steel coil springs which engage with the packing rings situated in
the grooves FF-This form of construction obviates the necessity of fitting the
cylinder extensions into the abutment Chamber L to contain the packing rings
surrounding the annular bore. It will be seen in Figure 26 that while the bore
of the Cylinder is annular in form it is an unbroken circle in cross section,
excepting that part which is fitted by the piston disc, which disc is packed steam
tight on either side by packing rings fitting in the grooves H H, which rings
shewn in Figure 3 are made for this form of Cylinder in a half circle and joined
together by tongue and groove or other similar devices, on the line where the two
sections of the Cylinder are joined-On the outside of the Cylinder near the hub
and over the packing grooves H H are formed bosses for the purpose of, being
bored out to contain the tempered steel coil springs which press against, the
packing rings in the grooves H H. These bosses are also provided with caps
screwed over or into them to furnish suitable end bearings for said coil springs.
Each section of the Cylinder is formed with projections E3. E3. which furnish
suitable supports for the thrust and main bearings of the abutment shaft N The
ears E2 are also formed on the outside of the two sections of the annual Cylinder.
In a double abutment Cylinder like Figures 24. 26. and 27 projections similar
to Es Es are cast on opposite sides of the ears E2 in order to, provide bearings for
abutment shafts on opposite sides of the Cylinder. This, form of Cylinder admits
of the application of a steam jacket as shewn in Figures 17 and 19. On the
outside of the sections or flanges which when the Cylinder is bolted together form
the abutment chamber L are secured pockets which with a cap upon, the, top are
shewn in Figures 1. 2 and 24, which pockets M' M' and cap M surround that part
of the abutment N not enclosed in the abutment chamber L by which means the
abutment or rings may be. removed without necessitating the taking apart of the
two sections of the annular Cylinder. The flanges of the cap forming the sides, of
the abutment. chamber are wider than the sections they are to cover and are formed
with a rim or projection on each edge of the inside face which fits closely over
the outer edges of the projections on the annular Cylinder surrounding the
Abutment Chamber L and so counteracts any tendency of the two sections of the

page_text: This
Cylinder from being thrown apart by the pressure of the steam between the
piston and the abutment-The double abutment Cylinders shewn in Figures 24. 26.
and 27 may be used in connection with one or with two pistons. When two
pistons are employed steam is admitted simultaneously between each piston and
the closed abutment in the rear of the piston and owing to the fact that the pressure
on opposite sides of the piston disc the cylinder and driving shaft is thus equalized
and balanced I am enabled to employ an immense pressure of steam without
danger of creating any unequal strain or increasing the friction or wear of the
moving parts. This form of constructing the Cylinder not only avoids the necessity
of forming a steam tight joint around the outer surface of the bore requiring more
labour and more strength of metal but simplifies the process of construction and
by the use of the special tool made for that purpose allows the Cylinder
to be completely finished inside without removing the tool therefrom."
engine may be constructed with two Cylinders with one piston in each
Cylinder and the Cylinders placed in such relation to each other as that
one abutment shall suffice for both Cylinders, the main shafts being so geared
together that the steam shall alternately fill each Cylinder and yet only
one abutment be required-The construction of the valve of this engine I will now
explain, 1 represents a Cylinder at the base of which is a foot 2 by which it is
secured to the Engine frame. Near the centre of the Cylinder 1 in front and
forming a, part of it is a hollow projection or pipe 3 through which pipe is a
shaft 4 extending nearly to the centre of the Cylinder 1. The inner end of such
shaft 4 is provided with a small bearing 5 which is located just beyond a spur
gear 6 whose outer diameter is not greater than the diameter of the shaft itself.
To the outer end of the shaft 4 is secured a mitre gear 7 which engages with a
similar gear 9 secured to the end of the shaft 8 running in a line parallel with the
length of the Cylinder 1 and at right angles to the pipe 3 for a purpose herein-
after explained. Nearly opposite the pipe 3 on the Cylinder 1 but close to the
flange 10 is a like pipe 11 provided with a rod 12. the outer end of which forms a
yoke 13 and the inner end of which is screw-threaded at 14. for the attachment of
the rod to a yoke for a purpose hereinafter described-On the opposite side of the
Cylinder 1-but near the centre of the same is the steam pipe 15 provided with a
Bange 16 by which it is connected with the supply pipe 17-The Cylinder 1 is
further provided with two detachable heads, the inner head 18 being provided
with pipe projections and flanges 19 and 20-19 is the exhaust pipe and 20 is the
supply pipes which conducts the supply of steam from the valve to the engine
cylinder to which it is secured by bolts passing through openings in the flange of
pipe 20 provided for that purpose into the flanges surrounding the ports on the
annular Cylinder-The opposite or front head 21 of the Cylinder 1 is provided
with a stuffing box 22 and gland 23 together with a bearing 24 to support the
valve shaft 25 Beyond the bearing on the shaft is secured the large spur gear 26,
which revolves the shaft 25. In Figure 32 the outside of the head 18 is shewn
while Figure 33 shows its inside form of construction-It is provided with two
ports 27. 27 which in form are sigments of a circular groove and are directly.
opposite each other and of uniform size. On one side of the head 18 is the
opening 19 into the exhaust pipe while a chamber 28 from the ports 27. 27 com-
municates directly to the supply pipe 20. The chamber 28 is arc shaped extending
partly around the head, the outer wall being cast on the outer surface of the head
so as to project therefrom while the inner wall is on a plane with the inner surface
of the Cylinder head. The inner wall is provided with openings forming the
ports 27. 27-Resting upon the finished inner face 29 of the head 18 is the
Oscillating reversing valve 30 which is also provided with two ports 31. 31.
identical in form size and position with the ports 27. 27 in head 18.-The flange
or projections in the face 32 of the reversing valve 30 engage with the finished
face 29 of the head 18-Extending around the periphery of the valve 30 on the
face 32 and also surrounding the ports 31. 31 and surrounding the hole 33 in the
centre of the valve 30 are the raised rims flanges or projections 34. 35. 36. which

page_text: are made to fit steam tight against the face 29 of the head 18. In the periphery
of the valve 30 is formed a cavity 37-see Figure 36 in which is fastened a
suitable device in the form of a link 38 Yoke 39 and screw 40 the latter
extending through the valve and link―The rod 12 is screwed into the yoke 39.
By reciprocating the rod 12 a partial rotary movement is imparted to the valve 30.
Upon the face 40 of the valve 30 are seen the ports 31. 31 and the central hole 33.
On each side of each one of the ports 31. 31 is located a recess or concavity 41 of
the same size as the ports 31 31 which recesses or concavities are formed by a rim
or projection identical in form with the rim surrounding the ports 31. 31 on the
face 40 of the valve 30-A like projection or flange surrounds the hole 33 in the
centre of the valve 30-In the hole 33 is nicely fitted the short stationary arbor or
pivot 42 which being tightly fitted within the central socket 43 of the head 18
furnishes a suitable pivot upon which the valve 30 turns when it is partly
revolved. The outer end of the stationary arbor 42 is made to fit within the
hole 43 in the end of the valve shaft 25 and furnishes a suitable end bearing for
the same Upon the face 40 of the valve 30 revolves the face 44 of the rotating
valve 45 which latter is provided with ports 46. 46 identical in form size and
position with the ports 31. 31 of the valve 30 and ports 27. 27 of the head 18.
The valve 45 is provided with a central opening 48 in which is cut a slot for the
reception of the feather 47 which fits within the groove 48 of the shaft 25. When
the shaft is inserted in the opening 48 and power is applied to the spur gear 26
the valve 45 is caused to revolve. Around the centre of the valve 45 between the
ports 46. 46 and central opening 48 are six openings 51 (more or less) through the
valve the purpose of which will be hereinafter explained-The face 44 of the valve
45 is finished to a fine true surface-On the upper face 47 of the revolving valve 45
will be seen the ports 46. 46 each of which is surrounded by a rim or projection
similar to ports 31. 31 in face 32 of the valve 30-The face 47 of the valve 45 is
also provided with radially formed grooves 49 as long as the width of the ports
46. 46, and their surrounding projections, and occupying all that part of the
valve face 47 situated between the adjacent ends of the ports 46. 46. An annular
groove 50 is formed in the face 47 of the valve 45 and is located within the outer
raised portion of this face. The radial grooves 49 communicate at their inner
ends with the annular groove 50-In the bottom of the annular groove 50 are
formed the openings 51. The intervening metal between the radially formed
grooves 49 is on a plain with the projections or flanges surrounding the ports 46. 46.
and with such projections are finished to a fine surface. Upon the top of the
face 47 of the rotating valve 45 is the cut-off valve 52 with its face 53 resting on
the face 47 said cut off valve being formed with two segmental sections 54 adapted
to cover the ports 46. 46. of the valve 45-On the face 53 of the segmental
sections 54 are formed radial cavities or recesses 55 which correspond in length to
the width of the ports 46. 46 and in width are adapted to be entirely covered by
the metal projections at each end of the ports 46. 46. when said projections are
made to pass beneath the same The metal extending between the segmental
sections and the hub of valve 32 is cut away at 56 to allow a free circulation of
steam underneath such part.
The hub 57 in the face 53 of valve 52 is adapted to fit over the hub of
value 45 and allow the same to freely rotate therein-On the face 58 of the
valve 52 the hub 57 is adapted to receive over it the worm gear 59 being secured
in proper position by the pins 60, 60. The end of the hub 57 fits within the end
of the socket 61 of the foot 62 which in turn furnishes the bearings 63 for the
worm 64 and the gear shaft 4. The foot 62 of the socket 61 is secured within a
recess on the head 21 by bolts suited to that purpose.-Having explained the
construction of the valve I will now describe its method of operation—The
flange of the pipe 20 is bolted to a like flange on the annular Cylinder of
the Engine and the foot 2 is secured to the engine frame while a spur gear
on the main shaft D of the Engine of one half the diameter of the valve
gear 26 is made to engage with the gear 26 by which means a revolving

page_text: ..
motion is communicated to the gear shaft 25 and the rotary valve 45-Owing to
the relative sizes between the gear 26 and the driving gear on the main shaft D
which actuates it-it will be seen that the valve is caused to revolve only one half
as fast as the main shaft D but owing to there, being two ports 46. 46. on the rotary
valve 45 and two ports 31 31. on the reversing valve 30 the valve 45 is only
required to make one half of a revolution to open and close the ports which
insures a fast revolution of the piston of the engine and a comparatively slow
motion of the valve 45-A greater number of ports may be used and still greater
difference of speed attained between the main shaft D of the engine and the
valve 45-The ports 46. 46 and 31. 31. are of such size that when the former are
revolved over the latter the cut off valve 52 being adjusted so as not to operate to
cut off. Steam would be admitted to the Cylinder of the Engine during one half
of a revolution of the piston, and in a double engine or a single cylinder with two
abutments and one piston-in which case two valves would be needed they being so
arranged on the valve shaft 25 that they would open and close alternately-a
constant application of live steam would take place during the entire revolution of
the main shaft Hence the cut-off being located in any desired position over the
ports 31. 31 of the reversing valve 30 causes the steam to be cut off at pleasure at
any point in the rotation of the valve. 45. which latter is located between the
cut-off 52 and reversing valve 30, whose upper face 40 constitutes the valve seat.
As already indicated the cut off 52 is operated by the worm 64 revolving the
worm gear 59 on the hub of the cut-off 52 which worm gear 59. is actuated
by the shafts 4 and 8 which latter is provided with a rack and pinion the rack
being secured by means of a right and left hand threaded screw 65 to the
rod of revolving governor balls (not shewn) which automatically operate the
movement of the cut-off 52. By uniting with this a device for connecting or
disconnecting the rack and pinion the cut-off may be made adjustable instead of
automatic. A hand wheel being secured to the shaft, 8 for that purpose-The right
and left hand threaded screw 65 is for the purpose of adjusting the cut-off to
secure any desired speed of main shaft of the Engine. It will be seen that the
face 44 of the rotary valve 45 which is finished to a fine surface revolves in contact
with the face 40 of the reversing valve 30 but owing to the rim or projection
around the ports and central hole a space is left between the main body of the
valve 30 and the face 44 of the valve 45 which space is constantly filled with
steam when the valve is in operation which steam passes through the openings 51
and counteracts the pressure of steam upon the face 47 of the valve 45 except
the space occupied by the ports 31. 31. and surrounding projections or rims and
also except the hub projections. When the end of the ports 46. 46 in revolving
approaches the near end of the ports 31. 31 of the valve seat so far as to make
an opening, steam would enter underneath the valve 45 into the ports 31. 31 and
would prevent cutting off steam before the rear parts of the ports 46. 46. had
reached the front part of ports 31. 31 were it not for the projections or rims around
the recesses 41. 41. These recesses being filled with steam at each half revolution
of the valve 45 not only counteracts the pressure of steam on the face 47 of the
valve 45 but renders it possible to cut-off steam at any desired, point of the
revolution without detriment to the balancing of the valve 45. It will be seen in
figure 31 that the ports 31. 31 of the reversing valve 30 are exactly conincident with
the ports 27. 27 of the valve head 18 so that steam passing through the ports 31. 31
will pass along the passage 28 to the supply pipe port 20 into the engine Cylinder thus
forming a continuous passage from the valve Cylinder 1 to the Engine Cylinder F
-As the direction of the rotating piston is determined by the application of steam
on one or the other side of the abutment when it is desired to reverse the engine
it is only necessary to so far oscillate or revolve the reversing valve 30 as to cause
the ports 31. 31 to pass out of range with the ports 27. 27 of valve cylinder head 18
by which means the projections around the ports 31. 31 on the face 32 of the
valve 30 will be brought in contact with the finished surface of the face 29 of
bead 18 out of range with the ports 27 27, hence no steam can pass through the

page_text: ports 31. 31 which are transformed into cavities or chambers which being filled
with steam very 'nearly balance the steam pressure 'on 'the face 47 of the valve 45.
so that while it continues to revolve it is relieved of friction 'or wear-By'thus
partly revolving the reversing valve 30 the recessed section on the face 32 is brought
over the ports 27. 27 of the head 18 causing a continuous passage from the Engine
Cylinder through the pipe 20 passage 28 ports 27. 27 recessed sections on the
face 32 of the valve 30 into the exhaust pipe 19 furnishing a means of continual
exhaust While' these changes are effected in the valve on one side of the abutment
of the Engine by which an inlet port is transformed into an exhaust port the same
movement changes an exhaust port into an inlet port on the opposite side of the
abutment——If it is desired to run the engine in both directions valves must be
placed on each side of the abutment and suitable devices employed by which both
valves may be operated at the same time and by the same movement. Hence the
valves will ultimately become supply or exhaust valves and the engine can be run
in either direction without interfering with the working of the automatic cut-off if
sucli is needed in both sides :-
Having fully described this invention what I claim as new and desire to secure
by Letters Patent is :—
'
..E
1
1917 C
..
Y
1st In a rotary Engine the combination with a revolving piston of a rotary disc
abutment arranged at right angles and suitable mechanism for imparting a con-
tinuous rotary motion thereto, substantially as shewn and described and for the
purposes herein set forth.
2nd. In a rotary Engine the Combination with a rotary piston disc of a rotary
abutment disc arranged at right angles to the rotary piston disc and suitable
mechanism for imparting a continuous rotary motion thereto and having the
periphery of said abutment disc arranged to snugly fit against the periphery of the
piston disc, substantially as shewn and described and for the purposes herein set
forth.
3rd. In a rotary engine the combination with a rotary piston disc having a
concave periphery of a rotary disc abutment arranged at right angles to the piston
disc and provided with a concave periphery and suitable mechanism for imparting
a continuous rotary motion thereto, substantially as shewn and described and for
the purposes herein set forth.
4th. In a rotary Engine the combination with a revolving piston and tapered
piston extensions of a rotary disc abutment arranged at right angles to the piston
disc substantially as shewn and described and for the purposes herein set forth.
5th. In a rotary Engine the combination with a self adjusting revolving piston
of a rotary disc abutment arranged to revolve at right angles to the line of move-
ment of said piston substantially as shewn and described and for the purposes
) herein set forth.
1
6th. In a rotary Engine the combination with the Cylinder provided with an
annular bore made circular in cross section of a rotary disc abutment arranged to
rotate at right angles to the annular bore and to open and close the same and with
suitable mechanism for transmitting a continuous rotary motion thereto substantially
5 as shewn and described and for the purposes herein set forth.
7th. In a rotary Engine the combination with a rotary piston disc of a rotary
disc abutment arranged at right angles to the piston disc and Cylinder extensions
located at opposite sides of said abutment and extending towards the centre of the
Cylinder substantially as shewn and described and for the purposes herein set
forth.
8th. In a rotary Engine the combination with a Cylinder and revolving piston
of a revolving disc abutment arranged at right angles to the revolving piston and
Cylinder extensions provided with self adjusting packing rings substantially as
shewn and described and for the purposes herein set forth.
9th In a rotary Engine the combination with a Cylinder and revolving piston
and piston disc of a rotary disc abutment arranged at right angles to the revolving
piston and cylinder extensions provided with self adjusting packing for packing
ป

page_text: the sides of the abutment and piston disc substantially as shewn and described and
for the purposes herein set forth.
10th. In a rotary Engine the combination with a rotary piston disc provided
with piston extensions and self adjustable piston located between the adjacent ends
of said extensions of a rotary disc abutment arranged at right angles to the rotary
piston and provided with an irregularly curved cut away portion for the passage of
said piston and piston extensions substantially as shewn and described and for the
purposes herein set forth.
11th. In a rotary engine the combination with a revolving piston of a rotary
disc abutment mounted on a shaft and arranged at right angles to the revolving
piston and devices for imparting vertical adjustment to said shaft and votary disc
abutment substantially as shewn and described and for the purposes herein set
forth.
12th In a rotary Engine the combination with a revolving piston of a rotary
disc abutment mounted on a shaft and devices for imparting longitudinal
adjustment to said shaft substantially as shewn and described and for the purposes
herein set forth
13th. In a rotary engine the combination with a revolving piston of a rotary
disc abutment mounted on a Shaft and bearings for receiving the end thrust of
said Shaft substantially as shown and described and for the purposes herein set
forth.
14th. In a rotary engine the combination with a rotary piston disc of a piston
provided with an expansible packing ring formed with a projection which fits into
a recess in the piston disc substantially as shown and described and for the purposes
herein set forth.
15th. In a rotary engine the combination with a rotary piston dise of a piston
connected therewith said piston being provided with an expansible packing ring
constructed with a projection that is split by a vertical and horizontal wall
substantially as shown and described and for the purposes herein set forth.
16th. In a rotary Engine the combination with the revolving piston disc of a
self adjusting piston and devices for counteracting the effect of centrifugal force
exerted on the piston substantially as shown and described and for the purposes
herein set forth.
17th. In a rotary engine the combination with a rotary piston disc of a piston a
weight lever and connecting links for counter balancing the piston substantially
as shown and described and for the purposes herein set forth.
18th In a rotary engine the combination with a rotary piston disc and a hollow
piston extension of a weight located in the hollow piston extension and links and
a lever for connecting the piston and weight substantially as shown and described
and for the purposes herein set forth.
19th. In a rotary engine the combination with a rotary piston disc and a lever
provided with an adjustable fulcrum located within a slot or opening in said piston
disc of a piston connected by a rod to one end of said lever and a weight connected
by a rod to the other end of said lever substantially as shown and described and
for the purposes herein set forth.
20th. In a rotary engine the combination with a rotating piston disc anda
piston provided with expansible rings of devices connected with the inner
expansible ring for counterbalancing the action of centrifugal force on the piston
substantially as shown and described and for the purposes herein set forth.
21st. In a rotary Engine the combination with the driving shaft and rotary
piston disc having conical recesses in the ends of its hubs of split conical rings and
bolts for securing the piston disc to the shaft substantially as shewn and described
and for the purposes herein set forth.
22nd. In a rotary Engine the combination with the main driving shaft and the
shaft carrying the rotating abutment arranged at right angles with the revolving
piston of intermediate gearing for transmitting a positive motion to the rotary

page_text: abutment shaft from the main driving shaft substantially as shown and described
and for the purposes herein set forth.
23rd. In a rotary Engine one section of the Cylinder having the projections Es.
cast solid there with said projections being constructed to receive the bearings of the
rotary disc abutment shaft arranged to revolve the said abutment at right angles
with the revolving piston substantially as shown and described and for the purposes
herein set forth.
24th. The combination with the packing rings of the Cylinder extensions of
devices for regulating the inward pressure on said packing rings substantially as
shewn and described and for the purposes herein set forth.
25th. The combination with the packing rings of the Cylinder extensions of the
springs L³ and adjustable wedges L³ substantially as shown and described and for
the purposes herein set forth.
26th. The combination with the packing rings of the cylinder extensions of the
block L¹ the Springs L³ wedges L' and set screws L substantially as shown and
described and for the purposes herein set forth.
27th. The rotary abutment disc cut away on one side for the passage of the
piston and cored out on its opposite side to balance the disc substantially as shown
and described and for the purposes herein set forth.
28th. In a rotary engine the combination with the annular cylinder and revolving
abutment of pockets secured to the opposite sides of the abutment chamber
substantially as shown and described and for the purposes herein set forth
29th. In a rotary Engine the combination with the Annular Cylinder and
revolving abutment of a cap secured to the top of the abutment Chamber and
adapted to form on either side surfaces suitable for the securing of the stuffing
boxes of the abutment shaft thereto substantially as shown and described and for
the purposes herein set forth.
:
30th. In a rotary engine the combination with the main shaft of Standards for
supporting the same said Standards formed in two parts the upper portions
constituting the lower half of the shaft bearings and provided with outwardly
projecting ears or flanges for the removable attachment of the caps of the Journal
box and secured to the lower Section of the Standard in a manner to prevent any
longitudinal displacement the upper portion of the Standards made both vertically
and laterally adjusted substantially as shown and described and for the purposes
herein set forth.
31st. The standards formed of upper and lower Sections the latter provided at
its lower end with a perforated supporting flange and at its upper end with a
supporting bracket and wedges interposed between said Sections of the Standard
and set Screws for varying the adjustment of said wedges and thereby raising or
lowering the upper section of the Standard substantially as shown and described
and for the purposes herein set forth..
32nd. The combination with the upper and lower sections of the main shaft
Standards of wedges provided with elongated slots, bolts inserted through said
slots for securing said sections together and set screws for varying the adjustment
of said wedges substantially as shown and described and for the purposes herein
set forth
33rd. A cylinder for rotary engines consisting of two sections having one or
more abutment recesses located at right angles to the bore and flanges between
the hub and abutment recesses for the insertion of bolts for fastening the Sections.
together substantially as shown and described and for the purposes herein set
forth.
34th. A cylinder for rotary engines consisting of two Sections each provided
with a semi-circular bore for the piston and a connecting Chamber for the piston
disc and furnished with abutment flanges in one or both sides and with flanges
between the hub and abutment flanges through which are inserted bolts for
securing the Sections together substantially as shown and, described and for the
purposes herein set forth.

page_text: 35th. A Cylinder for rotary engines consisting of two sections each provided
with a semi circular bore for the piston, a packing ring groove located on the inside
of the bore and with flanges between the hub and bore for the insertion of bolts
for securing the Sections together substantially as shown and described and for the
purposes herein set forth.
:
36th. A Cylinder for rotary engines consisting of Sections provided with inter-
locking lugs substantially as shewn and described and for the purposes herein
set forth.
37th. A Cylinder for rotary engines consisting of two Sections provided with
lugs or projections in their hub portions constructed to inter-lock and to allow the
Sections to be interchangable substantially as shown and described and for the
purposes herein set forth.
38th: A Cylinder for rotary engines constructed in Sections and provided with
an annular bore for the piston and intervening space for the piston disc the end of
the section being grooved around the bore, said groove extending to the opposite
sides of the space for the piston disc and provided with a series of pockets for the
reception of springs for keeping the packing rings pressed outwardly against the
revolving abutments substantially as shown and described and for the purposes
herein set forth.
39th. The combination with a rotary cut off valve of a rotary valve seated upon
the cut off valve the adjacent faces of the two valves being constructed to form
intervening steam space for balancing the rotary valve substantially as shown and
described and for the purposes herein set forth.
40th. The combination with a rotary valve provided with a steam space between
its lower face and seat of a rotary govenor valve seated on the rotary valve the
adjacent faces of the two valves being constructed to provide an intervening
steam space substantially as shown and described and for the purposes herein
set forth
on
41st. The combination with a rotary valve of a rotary governor valve seated
the rotary valve the adjacent faces of the two valves being recessed or grooved to
provide an intervening steam space and suitable devices for automatically actuating
the governor valve substantially as shown and described and for the purposes
herein set forth.
42nd. The combination with a Steam balanced rotary valve of a steam balanced
cut off valve serving as a seat for the rotary valve and a Steam balanced governor
valve seated on the upper face of the rotary valve substantially as shewn and
described and for the purposes herein set forth.
43rd. The combination with the head of the valve cylinder having ports formed
therein communicating with a Steam pipe or passage leading to the engine cylinder
of a cut off valve seated on the inner face of the valve cylinder head said cut off
being constructed with outwardly projecting flanges or ribs which encircles the
cut off valve and the ports formed therein substantially as shewn and described
and for the purposes herein set forth.
44th. The valve cylinder head constructed with a Steam passage cast on the
outer portion of the head the ends of the steam passage extending through and
forming steam ports on opposite sides thereof substantially as shown and described
and for the purposes herein set forth.
45th. The cut-off valve constructed with steam recesses or cavities on opposite
sides of the ports and of substantially the same size and form as said ports sub-
stantially as shewn and described and for the purposes herein set forth.
46th. The combination with the rotary valve provided with through ports of
the cut off valve constructed with ports and with steam cavities or recesses on
opposite sides of said ports the construction being substantially as disclosed whereby
the rotary valve is balanced and Steam cut off at any point of its rotation sub-
stantially as shewn and described and for the purposes herein set forth
47th. The combination with the rotary valve provided with radial grooves or
steam passages and an inner steam chamber connecting said grooves or passages

page_text: of a governor valve provided with radial recesses or grooves closed at opposite ends
substantially as shewn and described and for the purposes herein set forth.
48th. The combination with the rotary valve provided with a number of holes
for the passage of steam through the valve and an annular groove on the opposite
side with which said holes communicate of the rotary governor valve having a
grooved or recessed portion formed therein that registers with said annular groove
substantially as shown and described and for the purposes herein set forth.
49th. The combination with the governor valve of a worm gear connected thereto
by pins and a worm engaging said gear substantially as shown and described and
for the purposes herein set forth.
50th. The combination with the Governor valve provided with a hub, a worm
gear mounted on said hub and attached to the governor valve by pins, and a worm
for actuating the valve substantially as shown and described and for the purposes
berein set forth.
51st. The combination with the governor valve provided with a hub, of a step
secured to the head of the valve cylinder and provided with a recess for receiving
the hub of the valve substantially as shown and described and for the purposes
herein set forth.
52nd. The combination with the rotary.valve having radial bearing surfaces on
the back of the valve surrounding the ports therein of a governor valve provided
with radial grooves of less width than the width of the bearing surfaces at the
ends of the steam ports in the rotary valve substantially as shewn and described
and for the purposes herein set forth
53rd A rotary valve constructed with outwardly projecting. flanges around its
central openings and around its ports and on each end of the ports to form Steam
cavities or recesses on opposite sides of the ports and a Steam chamber in the
central portion of the valve substantially as shown and described and for the
purposes herein set forth.
54th. The combination with a rotary valve having a recess formed in its
periphery of a link and yoke secured within said recess by a screw and a rod.
secured to the yoke substantially as shewn and described and for the purposes
herein set forth.
55th. The combination with the rotary valve, and revolving shaft connected
therewith by spline and feather of the cut-off valve, and arbor or pivot extending
through the cut off and entering the end of said shaft substantially as shewn and
described and for the purposes herein set forth.
In Witness whereof I the said Herbert John Haddan have hereunto set my
hand and seal this twenty-third day of November A.D. 1882.