US772882A - Rotary engine. - Google Patents

Description

PATENTED OCT; 18, 1904.

W. A. E. HENRIOI.

ROTARY ENGINE.

APPLICATION FILED MAR. 21, 1903.

6 SHEETS-SHEET l.

no MODEL.

{ MMH PATENTED OCT. 18, 1904.

W. A. E. HENRIOI.

ROTARY ENGINE.

APPLICATION FILED MAR. 27, 1903.

6 SHEETS-SHEET 2.

NO MODEL.

PATENTED OCT. 18, 1904.

W. A E. HENRICI. ROTARY ENGINE.

APPLIOATION'IILED MAR. 27, 1903.

s sntms-snnnr 3.

KO MODEL.

110.772.882. PATENTED OGT. 18,1904.

W. A; E. HENRIGI.

ROTARY ENGINE.

APPLICATION FILED MAR. 27, 1903.

s SHEE -sum 4.

N0 MODEL.

No..7'72,882. BATENTED OCT. 18, 1904-. W; A. E HBNRIGL ROTARY ENGINE.

APPLICATION nun MAR. 27, 1003.

' 8 '6 sums-aunt s.

N0 MODEL.

g. 0 9. l 8 1 T G O .D E T N E T A P GE N EN HEv -Y u T 0 WR a l-rrm'oynon FILED 111mm, 1 903; 1 v I e suns-sum e.

N0 MODELI 7 Z & HN v v .v \V N UuNN W WWW? I UNITED STATES Patented. October 18, 1904.

PATENT ()FFICE,

ROTARY ENGINE.

SPECIFICATION forming part of Letters Patent No. 772,882, dated October 18, 1904.

Application filed March 27, 1903.-

T0 all whom, it may concern:

inder, the movement of the piston being effected by the admission of the motive fluid intothe cylinder behind the piston and between it and an abutment or diaphragm which is moved into and out of operative position in the cylinder, leaving the latter as the piston approaches it and being operatively positioned immediately after the piston has passed beyond it. For relativelylow piston speed reciprocatory movement of the abutment has been successful, because of the ample time afforded for the abutment movement; but when high-speed engines of this type are desired the time period for abutment movement as-. sumes such small proportions that the desired operation of the abutment cannot keep pace with the piston speed. Notionly this, but the rapid reversal of movemeht of the abutment gives rise to injurious strains and vibration in the apparatus, amost series objection in an engine of even very moderate size and power and increasing to a prohibitive degree with increased engine weight and power.

My present invention has for one of its objects the'production of a novelrotary engine or motor as a whole of compact and simple 4 construction and relatively light weight ca- V a very highefliciency.

pable of running at ahigh rate of speed with a minimum of ar or vlbration and possessing Another object of my invention is the production of a novel and efficient abutment or diaphragm which is given a positive inter-' at; Noi 149.797. N0 model.)

ductionof strong, durabIe, and efficient means for imparting to the abutment movement of the characterstated,the abutment being securely locked'in its operativeposition during the major portion ofjthe piston-stroke. The

abutment is maintained fluid-tight during ad- :mission of the motivefluid in a novel and very efficient though simple manner, and at the time the abutment is moved-to permit the passage of the piston it is either practically free .from or subjected to equalized pressure, so

that its movement consumes little power.

These and various other novel features of my invention will be fully described in the subjoined specification and particularly pointed out in the following claims.

I have chosen to show and describe herein my invention as embodied .in a compound engine or motor, the motive fluid being used eX pansively in the high-pressure cylinder and being'governed as to its admission thereto by a rotary valve which in this embodiment of my invention is mounted directly upon and operated by the main shaftof the engine. The

exhaust passes fromthehigh to the low pressure cylinder, and by a very novel construction thereof the piston traveling in the latter cylinder governs theadmission and exhaust thereof. My invention is not'restricted to a compound engine or motor, however, for, as

common to either a simple or a compound engine, and a practical embodiment of the invention in the latter type embraces or includes the former.

Various changes or modifications may be made in different features of the apparatus by those skilled in the art without departing from the-spirit and scope of my invention.

Figure 1 is a part front elevation and vertical section of a compound rotary engine or motor embodying one practical form of my invention, the sectional portion being taken on the line 1 1, Fig. 2, and showing the highpressu're abutment or diaphragm in operative position, the cylinder-jackets being shown in section to more clearly illustrate other parts of the apparatus. Fig. 2 is a top or plan view of the apparatus shown in Fig. 1, all of the .instant, as the high and low pressure pistons parts being in elevation, and the jackets are l omitted altogether for clearness of illustration. Fig. 3 is a left-hand end elevation of the engine or motor, showing the low-pressure cylinder and the means for controlling and operating the diaphragm or abutment cooperating therewith, the fly-wheel being omitted. Fig. 3 is a detail face view of the rotary valve for con rolling admission of motive fluid to the high-pressure cylinder. Fig. 1is a transverse sectional view of the low-pressure cylinder on the line 1 4., Fig. 2, looking toward the right, the piston and the shaft of the abutment being in elevation. Fig. 5 is a similar view of the high-pressure cylinder, its piston and abutment, and some of the adjacent parts on the line 5 5, Fig. 2, looking toward the left, but not taken at the corresponding in actual practice are set one hundred and eighty degrees apart on the main shaft. Fig. 6 is an enlarged side elevation of the lowpressure piston and the hub to which it is secured. Fig. 7 is an end view thereof looking toward the left, Fig. 6. Fig. 8 is an enlarged detail, in side elevation, of the high-pressure piston, its hub being broken olf. Fig. 9 is a detail'on the line 9 9, Fig. 2, looking toward the right, of the means for controlling the movement of and for locking the high-pressure abutment, the time chosen for illustration being just at the instant when the abutment is unlocked and its movement is just about to be effected. Fig. 10 is a similar view of the same means, but taken when the abutment is just at the center of its movement, the speed-accelerating cam being shown in dotted lines in Figs. 9 and 10. Fig. 11 is a face view of the speed-accelerating cam, the view being taken on the line 9 9, Fig. 2, but looking toward the left. Fig. 12 is a sectional detail on the line 12 12, Fig. 2, looking toward the right, of the controlling-cam for the low-pressure abutment, showing the lockingsegment and the knuckle-arm support or carrier for the cam-follower to be described. Fig. 13 is an enlarged detail, partly broken off to save space, of the abutment or diaphragm which is moved into and out of the cylinder, the upper end of the abutment being shown in section. Fig. 1 1 is a longitudinal sectional View of the abutment on the line 1 1 14, Fig. 13. Fig. 15 is a longitudinal sectional detail on the line 1 1, Fig. 2, through the longitudinal axis of the main shaft of the motor to show clearly the jacket-supports and jackets for both the high and low pressure cylinders, the jackets having been omitted in the preceding figures to avoid confusion. Fig. 16 is an enlarged sectional detail on the line 16 16, Fig. 6, showing the packing member for one of the extensions or shoes of the low-pressure cylinder and the manner of supporting it on the extension; and Fig. 17 is an enlarged perspective detail showing the separated ends of one of the expansible packing-rings carried by the high-pressure piston to be described in detail.

In Figs 1 and 2 1 have shown the operative parts of the engine or motor as mounted upon a heavy rigid base A of suitable size and shape and preferably made as a casting, said base having bolted to it the various stamlards or other supports for the operating parts of the apparatus, and as l have shown a compound engine comprising a high and a low pressure cylinder each with its abutment and piston and the means for eliecting the proper movement of the abutment 1 will describe such compound engine, and it will appear hereinafter that the high-pressure end of the engine contains all of the essentials for a sin gle expansion-engine. For conveniei'lee of construction the cylinders are made in four sections or parts, provided with external flanges, as 3 and 1, and rigidly connected by suitable bolts, the cylinder-sections being internally grooved, so that when the said sections are assembled the high-pressu re cylinder (indicated as a wholi at ll) will present an annular piston-chamber H hereiintlter referred to as the cylinder, and in which the piston travels. The flanges 3 and -1-a re formed with concentric inner and outer ribs, as 3*, (see Fig. 5,) the said ribs being machined and ground to make absolutely fluid-tightjoints when the cylindersections are assembled without requiringadditional packing and reducing the amount of machining and grinding necessary. As best shown in Fig. 15, the cylinder-sections are shaped to present a heavy lirm bearing H for the main shaft B", which extends transversely through the cyl i n der, its longitudinal axis forming the center of the piston-chamber proper, ll 'llmouter face of the bearing H is circularly recessed at /t' to form a seat for an :ubnission-valve for the high-pressure cylinder, (shown separately in Fig. 3,) the valve being shown as a disk V, having its hub e keyed to the main shaft V and provided with a segmental slot Fig. 3. An inlet passage or conduit (see Fig. 1) in the lower part of the bearing ll connects the valve recess or seat /t with the inlet-port A". (See dotted lines, Figs. 1 and A cover-plate l1." is bolted to the bearing portion H after the valve V is in place, coinpleting the cham| cr in which the valve. rotates, said cover-plate having an inlet porter conduit h, registering with the outer end of the conduit H, to receive motive fluid from any suitable generator or source of supply. (Not herein shown.) The valve-disk V rotates between the opposed and adjacent ends of the conduits b /1/, and except when the segmental admission-opening r passes between the conduits the admission et motive fluid to the cylinder is cut oil. l have provided simple and ellicient means for preventing the escape of motive iiuid at the inner end I fitting easily into annular seats b and It in character.

the part H of the cylinder-casting and in the cover-plate H respectively. These rings are yieldingly maintained against the opposite faces of the valve-disk by admitting the motive fluid to the annular seats 7L5 and 72 and in Fig. '1 a small duct 6 is shown leading into the latter seat and a duct 5 into the seat it. 1 have not shown any connection between these ducts and the fluid-supp] y, as such connection would be by piping of any suitable The rings 5 and 6 are annularly grooved on their inner and outer peripheries to receive packing of, any suitable character, which packing will bear against theinner and outer walls of the ringseats, preventing motive fluid from creeping around the rings. By such packing device I obviate a forcible wearing friction upon the opposite faces of the valve-disk, while eifectually preventing leakage at the admission-conduit it. The parts of the cylinder-castings which form the shaft-bearing H are cored out, as at 7 and 8, Figs. 1 and 15, to prevent heating of the shaft-bearing, which might occur by reason of the jacketing of the cylinder hereinafter to be referred to.

Referring now to Fig. 15, it will be seen.

that the opposed faces of the two upright halves of the high-pressure cylinder are separated within the piston path or chamber H to leave a clearance 7L7 and a hub-socket-h for the high-pressure piston-disk and its hub. as

will be apparent from. an inspection of Fig. 1, in which latter the piston-disk and its hub are shown in place secured to the main shaft;

The piston-disk it has an enlarged hub h,-

is reduced to a minimum. Annular seats it and 7& are formed in the inner faces of the cylinder-sections concentric with the pistonchamber and of-such'radius that rings 11 and '12, inserted in the seats, will bear upon the opposite faces of the piston-disk near the periphe-ry thereof. These rings are shown inposition in Fig. 1, and they are yieldingly maintained in contact with the piston-disk by motive fluid at a relatively low pressure, admitted to the seats beneath the rings through ducts 11 and 12 Figs. 1 and 15, these ducts 1 terminating in nipples to which suitable pipes can be attached communicating with. the

source of. supply for the motivefluid. If the.

pressure of the latter is considerable, as will he usually the case, asuitable reducing-valve of any desired or well-known construction would be introduced between the source of supply and the ducts to so reduce the-fluidpressure that the rings lland 12 would bear against the opposite faces of the disk it with a light pressure. The rings 11 and 12, which are metallic and continuous, are grooved on their inner and outer peripheries, as shown in Fig. 1, to receive suitable packing, preferably expansion or split rings,.whicl1 will bear on the inner and outer walls of the seats h and 72, to thereby prevent the escape of the motivefiuid from the piston-chamber along the faces of the piston-disk. It will be manifest that a tight packing can thus be effected without exerting any undue friction upon the piston-disk, it being my object to avoidsuch friction wherever possible.

The high-pressure piston P'is preferablya casting circular in cross-section and of suchdiameter that it will fit easily the chamberI-I of the cylinder. longitudinally-divided halves, each half on its inner face being recessed, as at P, (see Fig.

8,) toreceive a radial extension it of the piston-disk, and bolts 14, passed a transversely through the piston and the extension 7t, rigidly connect the parts of the piston to each otherand tothe disk. Any outward movement of the piston due to centrifugal force is counteracted by its rigid connection described The piston is made in two with the piston-dislgand the latter, it will be remembered, is rigidly secured to the main shaft. The piston is provided with external seats or recesses 19, two of such grooves being shown, each to receive a split expansion pack ing-ring 19 the separated ends of the rings coming up on opposite sides of the piston-disk.

When the piston is in the annular chamber H the expansibility of the rings p causes them to bear against the side walls of the chamber and effectually packs the piston, it being understood that the rings fit in the grooves 19 fluid-tight. In Fig. 8 one ring is shown in place, andthe nearer half of the other ring is cut off to show the groove for the ring and also to show a locking lug or projection 19 in the groove, one of these lugs being formed at each side of the piston-disk. The separated ends of the packing-ring are .cut out, as at 19 (see Fig. 17,) to receive the lugs, the latter-assisting in keeping the rings in proper position and forming abutments against which the side portions of the cutaway parts 11 hear at the separated ends ofthe rings to prevent leakage at such points. It will be manifest that the expansion-rings i 9 will pack the piston from one to the other end of each ring; but as therings are ex- .pansible their opposed ends will not bear tightly against the faces of the piston-disk,

:a slight clearance through which the-motive fluid could pass were means not provided to prevent it. To prevent leakage at the points indicated, the opposite faces of the pistondisk are radially grooved, as at 15, Fig. 8, each to receive a yielding metallic packing member 19 secured at its inner end by rivets 16 to the disk, its outer end extending up to the wall of the piston, and such free end of the packing member p" is bent up so as to project slightly beyond the face of the disk. When the parts are in operative position, the free ends of the two packing members 1)" bear against the opposite walls of the clearance 71/ and between the packing means p effectually preventing the leakage of any fluid from one to the other end of the piston at the ends of the rings adjacent the piston-disk.

The inlet or admission port 71. of the highpressure cylinder is formed in the outer cyl inder-half, and the outlet-port I?" (see Fig. 5) is made in the opposite or inner half of the cylinder, so that the admission and outlet or exhaust ports are located on opposite sides of the piston-chamber or cylinder, but not directly opposite each other, as will be clear from an inspection of Fig. 5. Between the ports the cylinder is provided with a transverse passage intersecting the chamber H for the admission of an abutment which when in its operative position forms the head or passage, one of the faces, as 18, being shownin said figure, and the passage itself is indicated at it, Fig. 5; hen a rotary engine is run at high speed, it will be manifest that the movement of the abutment out of the piston-path must be effected with great rapidity, the speed of the abutment movementincreasing with the speed of the engine, and one of the most important features of my present invention resides in the abutment movement and the means for effecting and controlling such movement. The smaller the are through which the piston moves during the withdrawal of the abutment from and its movement into the piston-path the greater will be the efliciency of the engine, and in my present invention the abutment is moved out and in while the piston travels through an arc of forty-live degrees or during one-eighth of the entire pistonstroke. 1 have provided means to impart an intermitting rotary movement to the abutment, and the movement is positive and exact, While the abutment is positively locked when in its operative position in the pistonpath. The abutment is shown on an enlarged scale in Figs. 13 and 14 and comprises a hub a and two diametrically opposite wings or extensions a, which terminate in nearly-circular enlargements (0 these enlargements having accurately machined and ground faces a walls 18 of the abutment passage-way a in the cylinder. in the smaller figures the faces m are not shown, owing to thesmall scale of the drawings. Theouter eml of each abutment proper, as the part a? may be termed, is areshaped at 1/", the center of the are being coincident with the axial center of the hub 1/, and an elongated recess a is formed in such portion of the abutment to receive a yielding metallic shoe cf, secured at one end at 1/ in the recess. \Vhen an abutment is in its operative position in the piston-path, the shoe bears against the periphery of the rotating piston-disk a", and at such time the shoe acts to pack the end of the abutment and prevent leakage of fluid between the abutment and the edge of the piston-disk. An annular groove 1/. is made in one face of the hub u, and such face is at the exhaust side of the abutment.

Referring to Fig. 5, the. high-pressure abutment is mounted on a rotatable shaft (1", below and at right angles to the main shaft H, the shaft having a I airing in a partof a casting forming a housing or chamber in which the two connected abutments move in a. circular path. The housing is made in four parts, and preferably two parts are made integral with the lower cylimler-sections. The abutinent-chamber is shown at A, Figs. 1, 5, and 15, and the several parts of the casting are bolted together, as at 2o 21, the parts A being integral with the cylinder-sections, while the parts A" are made separately and bolted together. A keyway (1 is formed in the abutment-hub (I to receive a spline or feather a, Fig. l, in the shaft 1/", so that the connected abutments will rotate with the shaft a"; but they are permitted a slight bodily movement longitudinally of the shaft for a purpose to be described. The almtment-housing opposite the ammlar groove u in the abutment-hub is provided with an internal annular seat a, Fig. 5, to receive a coiled spring e which also enters the groove u, the spring normally tending to center the abutment with relation to the opposite faces 18 of the passage-way lt Supposing now that one of the almtments is in its operative position in the piston-path and that the piston has passed beyond the abutment, motive lluid being ad mitted to the cylinder through theport a between the abutment and'the rear end of the piston. The pressure of the fluid acting against the abutment oppositely to the force of the spring a forces the abutment against the face of the passageway ]z. on the exhaust side, and thereby absolutely seals the exhaust side of the cylinder, so that none of the tluid admitted from the inlet-port can pass the abutment. The admission of the motive lluid, it will be remembered, is governed by the opening 1- in the disk-valve V, admission taking place so long as the opening w permits the tluid to pass on opposite sides to pass between the faces or l from the inlet-conduit A to the cylinder, cutofif being effected as soon as theimovement of the valve V has carried the inlet-opening o beyond such conduit.

. travel through the annular cylinder in wellknown manner. the exhaust fluid being discharged from the cylinder ahead of the pisoff the admission, so thatthere is no commu ton through the exhaustport 7L As the piston is about completing its stroke the abutment must be moved out of its path, and I have so arranged the mechanism that the abutments alternate with each other in the cylinderthat is to say, as the piston approaches the end of its stroke the abutment then in the cylinder is moved out of the piston-path at one side of the cylinder and the diametrically opposite abutment is brought into the piston-path from the opposite side of the cylinder, the piston passing the passageway 72. while the connected abutments are rotated through one hundred and eighty degrees. The abutment movement therefore is always in the same direction, and each movement of an abutment is through an arc of one hundred and eighty degrees, and the means by which this movement is effected will be described in detail. By employing two abutments the engine can be speeded up to a very high rate, amply sufficient time for the passage of the piston being provided during the extremely short period that both abutments are out of the cylinder. hen the abutments are out of the cylinder, .the imperforate portion of the valve-disk V shuts nication between the admission and the exhaust of the cylinder. It should be stated here that the fluid-pressure decreases from the beginning to the end of the piston-stroke,

.move the abutments does not have to overcome the pressurewhich acted upon the abutment during the major portion of the stroke to hold it against the exhaust side of the abutment passage-way. As soon as the pressure .on the opposite sides of the abutment is equalized, and such equalization is at sub- I stantially the instant when the abutment is about to move, the spring 3 can operate to center the abutment with reference to the side walls of the passage-way 71 The abutment chamber A is made fluidtight, so that any leakage of the admitted fluid on the admission side of the abutment small and in no way affects the operation of the engine.

The higlrpressure cylinder is connected with the base A by standards A A, which can be integral with portions of the cylinder or separated therefrom, as may be most convenient or desired.

The abutmen t-shaft a after passing through the abutment-housing is shown as provided with a bevel-pinion a, Fig. 2, in mesh with' a large bevel-gear a, fast on a shaft (4 supported in a bearing a on the standard A Said shaft has secured to it a transmitting member. or disk (0 provided with radial slots a, six of such slots being herein shown, and the portions of the disk between theslots are I provided with concave locking-seats (0 for a purpose to be described, the slotted disk or transmitting member forming a species of star-wheel. ranged oppositely to a locking device or segment b fast on a counter-shaft b, rotatably mounted at its ends in bearings at c Fig. 2, the former bearing being carried by the standard'A while the latter is mounted ona standard tobe referred to, which partly supports the low-pressure cylinder. The counter-shaft 6 passes through two standards D and E, rigidly bolted to the base A and between said standards a gear B is secured to the countershaft, said gear meshing with a second gear B, fast on them'ain shaft B between the high and low pressure cylinders, as shown in Figs. 1 and 2. The locking-segment b as shown in Figs. 9 and 10, has a circular pe- The periphery of the disk is ar I ripheral portion which is adapted to co6perate successively with one after another of the seats (0 of the transmitting member duringa portion of each revolution of thecounter-shaft b.- The remainder of the locking-segment is incurved, as at 7), to permit the partial rotation of the transmitting member, and in the construction shown herein said transmitting member makes one-sixth of a revolution for each revolution of the counter-shaft. The latter has fast upon it an elongated hub between the locking-segment and the standard D, said hub having a'rigid radial arm 6 to which is pivotally connected at or near its outer end, as at 6*, a swinging arm 6.

An actuator, shown as a pin Z), is extended transversely through the enlarged free end 71 of the swinging arm 6' and projects at each end, as shown best in Fig. 2, the end of the actuator nearer the transmitting member being provided with a roll 6 (see dotted lines, Fig. 2) to easily enter one of the radial slots 0 of the transmitting member. The opposite end of the actuator is provided with a cylindrical enlargement b to cooperate with a speed-controlling device, herein shown as a cam-groove (Z, formed in the face of the circular head or enlargement D of the standard D. Referring to Figs. 9, 10, and 11, the camgroove is shown as circular for a little more than one-half its extent, andthen it presents two straight portions d, which are substantially tangent to the circular part of the groove, terminating at the high portions 6Z5. Be-

tween the high portions the cam iscompleted by a straight part (Z In Fig. 11 the partlydotted and partly-dash line indicates the path of travel of the center of the enlargement I). In Figs. 10 and 11 the relation of the camgroove to the transmittingmember is clearly Shown.

It will be manifest that the actuator 6 revolves bodily with the counter-shaft 7), and it also has a movement toward and from such shaft, owing to the pivotal connection of the actuator-arm 7) with the arm I), which is ra dial to the counter-shaft. The direction of rotation of the latter is shown by the arrow 30. Figs. 9 and 10, the transmitting member e turning in the opposite direction, as shown by arrow 31. In Fig. 9 the parts are shown in such position that the enlargement I) is in one of the tangent portions (Z of the cam-groove, while the roll of the actuator is just entermg one of the radial slots 0/ of the transmitting member, and it will also be seen that the next slot above is in alinement with the upper straight portion (Z of the can1groove. Now as the counter-shaft Z) continues to revolve it will be manifest that not only will the roll 6 travel along the slot (0 toward the center of the transmitting member, but it will be moved nearer to the center thereof by reason of the high portions (Z of the cam than would otherwise be the case. At the mid-portion of the advanced movement of the transmitting member, which is shown in Fig. 10, the enlargement 72 is at the middle of the straight part (Z of the cam-groove and the roll 71 is then nearest the center of the transmitting member, and consequently moves it ,With an accelerated speed. 1f the groove (Z was a continuous circle, the member a would still be moved through one-sixth of a revolution for each revolution of the counter-shaft; but by shaping the cam-groove as herein shown the speed of movement of the member (4 is accelerated. The tangent portions (5 of the cam-groove permit an easy entrance and exit of the actuator from one of the radial slots of the star-wheel without any jar or hang, and as the movement of the star-wheel is about to begin the depressed portion 7/ of the locking-disk is in such position as to permit this movement, the segment unlocking the star-wheel at the instant that its movement begins. At mid-movement the lockingsegment is in the position shown in Fig. 10, and as the star-wheel movement is completed the rotation of the counter-shaft causes the locking-segment to move into locking engagement with the next following locking-seat to hold the star-wheel absolutely immovable during the remainder of the revolution of the counter-shaft and the actuator carried thereby. The stepbystep or intermittent movement given to the star-wheel is transmitted through the shaft a to the bevel-geara and from it to the pinion e and the abutment-shaft a",

the parts being so proportioned that each sixth revolution of the star -wheel imparts onehalf a revolution to the abutment-shaft a" to thereby move one abutment out of the piston-path and the other abutment into the piston-path after the piston has moved by. It has been stated that I desire to effect the abutment movement during one-eighth of the pis ton-stroke, and remembering this it will be manifest that the star-disk alone moving one-sixth of a revolution at a time would necessitate the employment of one-sixth of the piston-stroke for the abutment movement. That would be equivalent to a clearance of thirty degrees on each side of the abutmentpassage in the cylinder. By accelerating the speed of the star-wheel as has been described the abutment movement is speeded up, as it were, so that it will take place while the piston travels through one-eighth of its stroke, or an arc of forty-five degrees. At the instant that an abutment reaches operative position in the cylinder the centerof the piston istwenty-two and one-halfdegrees beyond it; but the actual distance or clearance between the alnitment and the rear end of the piston is this twentytwo and one-half degrees less the length of the piston between its center and its rear end. The admission of motive fluid into the cylinder is so regulated by the valve V that no lluid enters until an abutment is in full operative position and the rear end of the piston beyond the after end of the admission-port a". If the bevelgear a has forty-eight teeth and the pinion (1. has sixteen teeth, it will be manifest that each advance of the transmitting member 11"" will be equivalent to eight teeth of the gear a and the pinion 14 will be moved through one-half of a revolution.

The counter-shaft 7) is rotated positively from the main shaft B by or through the intermeshing gears B" B, hereinbefore referred to. There is thus a constant and positive control of the abutment movement from the main shaft. The faster the speed of the latter the more rapidly will the abutment movement take place and always in proper timing with relation to the piston.

So far as a single engine or motor is concerned the apparatus so far described is romplete, as will be obvious to those skilled in the art, and I will now describe in detail such parts of the low -pressure end of the engine as may be necessary to a full understainling thereof. Before noceeding to such description, however, it should be stated that in practice the actuator o is rotatably mounted in the enlargement or boss o of the swinging arm and to reduce friction it is convenient to mount the actuator to rot-ate on ball-bearings, and referring to Fig. 2 such ball-bearings may be located at 32) in the boss If". It will be obvious that instead of enlarging one end of the actuator, as at I), and mounting a roll,

as If, on the other end 1 could mount a roll ator which follow the cam-groove and cooperate with the transmitting member or starwheel, respectively. g

As with the high-pressure cylinder I. prefor to make the low-pressure cylinder in sections bolted together substantially as described for the high-pressure-cylinder, and the low-pressure cylinder is indicated as a whole at L, it being provided with an annular piston-chamber L of greater cross-sectional diameter, however, than the high-pressure chamber H this being clearly shown in Fig. 15. The main shaft B passes through and is supported in a lateral bearing portion L, (best shown in Fig. 15,) and the cylinder-sections are provided with annular packing-ring seats ber save that it is larger, and for that reason it needs no further detailed description, the abutment-hub being indicated in Fig. 4: at m and the diametrically opposite abutments being in dicated at m The hub is mounted to rotate with the abutment-shaft'm, and it is also slidable longitudinally thereof by means of a spline or feather m. On the exhaust side of the'abutment-hub I- have located a spring 8 to center the abutment, the spring being com-.'

pressed, as herein described. when the motive fluid is admitted to the low-pressure cylinder behind its piston. An abutment chamber or housing M is operatively connected with the low-pressu re cylinder, said housing being made in sections, as clearly shown in Fig. 15, and connected by suitable flanges M The housing is provided witha stuffing-box at M for the abutment-shaft, the outer end of "the latter having a bearing m secured to or forming part of a standard M which connects one side of the low-pressure cylinder with the base-plate A a second standard M being provided on the opposite side of the cylinder.

The general construction of the low-pressure cylinder and abutment-housing is well shown" in Figs. 1 to 4, inclusive, and Fig. 15.

A bevel-pinion mi on the abutment-shaft meshes with-a bevel-gear m, fast on a shaft m, parallel to the main shaft B a bearing m supporting the shaft on, the latter being provided with a transmitting member or stardisk 771, in all .respects corresponding tothe star-wheel c0 9, hereinbefore described, operating in connection with the high-pressure cylinder.

The counter-shaft b, which.it will-be remembered, is supportedin the bearings a a, carrles a locking-segment a similar to the segment b and cooperating with the lockingseats m of the disk m which has radial slots m to be entered by the revolving actuator, to be described. Between the locking-segment 77% and the enlarged head E of the stand E a hub 42. is rigidly secured to .the counter-shaft Z), said hub having a radial arm n on the free end of which is pivotally connected at 72* a swinging arm a enlarged at its free end to form a boss at. v

The actuator a, one end thereof being shown in dotted lines in Fig. 2, extends through the boss a and is rotatably mounted therein, as described in relation to the actuator b, and one end of said actuator, as M, (see Fig. 12,) is cylindrically enlarged to interinittingly enter and depart from one of the radial slots m of the transmitting member 777/ The opposite end of the actuator is provided with a roll a (see dotted lines, Fig. 2) to enter acam-groove e in the adjacent face of the head E." The shape of the cam-groove is clearly shown inv Fig. 12, and it will be noted that it diflers from the cam-groove shown in Fig. 11 in that it is circular for the greater portion of its length and then is made as a straight portion or chord connecting the ends of the circular portion.

Whereas the cam-device shown in I Fig. 11 and for the high-pressure cylinder is i an accelerating device the cam shown in Fig. 12 acts to retard the speed of angular movement of the star-wheel m the straight portion 0 of the camroove moving the actuatorfarther away from the center of-the starwheel, so that the speed of the latter is slowed down. This in connection with thelow-pressure cylinder is necessary in the present embodiment of my invention owing to the greater distance between the extreme forward and rear ends of the low-pressure piston, to be de scribed. In other respects, however, the operation of the parts between the counter-' shaft 5 and the abutment-shaft m is similar to that hereinbefore' described in connection with the high-pressure cylinder.

The admission-port for the low-pressure cylinder is shown at Z in dotted lines, Fig. e1, because itis formed in the side of the cylinder which has been removed in such view, while two exhaust-ports Z and Z are provided at opposite sides-of the cylinder and offset one from the other, the port Z being formed in the cylinder side wall. (Shown in Fig. 4.) The abutment-passage Z is between the two exhaust-ports and the inlet-port Z In Fig.

intoaboss Z (see partly-dotted lines, Fig. 4,) and in actual practice the bosses 1 Z would be connected by a Y-coupling communicating with the main exhaust conduit or pipe. the latter not being shown here, as it would tend to confuse the drawings and really forms no part of the invention. The motive fluid when exhausted from the high-pressure cylinder passes from the port k by means of a pipe it. (see dotted lines, Fig. 1,) and preferably in practice the exhaust would be conducted through a series of coils to be superheated before being permitted to pass through a pipe Z, Fig. 1, to the boss Z connecting it with the admission-port Z.

The low-pressure piston G is cylindrical in cross section and preferably made in two halves recessed to receive a radial extension Z of the piston-disk Z, and the extension and the'two parts of the piston are rigidly held together by suitable bolts 80, Fig. 4. Packing-rings 71 are mounted in annular grooves in the piston and cooperate with the cylinderwalls to prevent the leakage of motive fluid, one of the grooves being shown at 7, Fig. 6, the packing-ring being broken off to show the groove. Locking-lugs are formed on the piston to cooperate with the separable ends of the expansible packing-rings, the latter being shaped substantially as shown in Fig. 17. To prevent leakage of fluid between the upper and separated ends of the packingrings and the piston-disk 7)", I provide on each side of the latter a radial groove to receive a flexible metallic packing-strip which bears against the cylinder-wall, and thereby prevents leakage at that point. I have so constructed the low-pressure piston that it serves in a manner as a valve to control the admis' sion and exhaust ports to prevent any communication between said ports when one abutment is moving out of the cylinder and its fellow abutment is about to move into it, and to this end the piston is provided with curved and oppositely-extended extensions and The extension is located at the leading end of the piston and the extension g at its rear end, said extensions being substantially concaveconvex in cross-section and cooperating with opposite walls of the piston-chamber L -that is to say, the shoe or extension will act successively with relation to the exhaust-port 1 and the inlet-port Z while the extension 5 will act in connection with the exhaust-port Z Referring to Fig. 4:, it will be seen that as the piston advances in the direction of the arrow the extension will cover and close the exhaust-port Z just about the time that the main body G of the piston will close the other exhaust-port Z and at this instant the abutment is moved out of the cylinder to permit the passage of the piston across the abutment-path. At that instant the inlet-port Z is opened, and were it not for the extension there would be established a very direct communication through the chamber L between the inletport and the exhaust-port P". which of eourse would be prohibitive. Now as the piston advances the inlet-port will be closed by the extension f, and the extension y will art to keep the port l closed until the extension has passed beyond it, the body of the piston keeping the port l' closed. As the piston advanees farther the rear end of the extension moves beyond the abutmentpath, the inlet-port then opening as the rear end of the body of the piston passes beyond it: but at this time the incoming abutmententers and assumes its operative position in the cylinder, so that the. fluid admitted through the port W cannot pass to the exhaust-ports because of the. interposed abutment, and such fluid operates at the bark of the piston to drive it forward.

To avoid machining and grinding the convex faces of the extensions and r l have provided metallic packing-strips for each extension, and the packing p is shown in the drawings for the extension This packingstrip is made substantially L-shaped in crosssection (see Fig. 1(5) and rests in a groove or seat formed in the extension, said groove having an offset recess to receive any suitable soft packing, as p, Fig. It), to prevent leakage around the packingmember p The latter member extends along the inner and outer edges, and the end of each extension in practice abuts against th. adjacent packingring 1).

The inlet-port for the low-pressu re cylinder is in continuous con'nnunimith n with the ex haust side of the high-pressure ovlinder except at such times as the passage of the lowpressure piston closes the inlet as has been described.

By the construction of the lo\\'-pressure piston herein shown and described I avoid the use of a separate valve to cooperate with the admission and exhaust ports at certain parts of the stroke. \Verc it not for the extensions the ports and I would be in communieathm when the piston crossed the al mtment- )assage: but at that time the extension g covers the port f and keeps it covered until the extension covers the inlet-port I.

The high and low pressure pistons are set opposite each other on the main shaft to balance the load, the piston-weight's beingequalized as much as possible. Any inequality of weight can be counterlmlamsed by appropriately weighting the fly-wheel \V.

l have provided means between and supported by the high and low pressure cylinders to take up end thrust of the main shaft, so that there will be no longitudinal movement of the latter. Struts 102. secured to the inner end of the bearing L, are rigidly bolted to a heavy ring-carrier L Figs. 1 and 2, through which the shaft passes. the inner face of the ring being recessed to receive a hardened-steel bearing-ring L Fig. 1, upon which travel the jacket.

conical hardened antifriction-rolls 102. The hub of the gear B has secured to its adjacent end a bearing-ring L, which rests upon the conical rolls 102, the heavy ring-carrier L thereby taking up any end thrust to the left, viewing Figs. 1 and 2. On its opposite end the hub ofgear B has an attached hardened ring H for a second set of conical rolls 104C, and an opposing fixed ring H is secured in the recessed end of a ring-carrier H bolted to struts 106, secured to the inner end of the bearing H, forming a part of the high-pressure cylinder H. By the end -thrust bearing last describedmovement of the main shaft to the right is prevented, and the rolls described prevent any undue friction on the end-thrust bearing.

In Figs. 1 and 15 I have shown jackets for the cylinders, and these jackets are preferably made in two parts for each cylinder. For the low pressure cylinder the parts J and J which may be castings, are provided with partly-circular flanges j and ,7" to be secured to an annular flange or face of the bearing L by screws 120 122, while the separated ends of the jacket parts. are flanged at ,7? to be secured to the outer walls of the abutment-housing M at 123 and 124. The meetingedges of the parts J and J overlap and are connected by screws 125. Thus the low-pressure cylinder is completely inclosed by the jacket with the exception of the part of the cylinder which extends through the housing M. In practice a non-heat-conducting lining (not shown and of any suitable character) may be applied to Similar jacket members J and J are applied to the high-pressure cylinder. The jackets will be placed in communication with the outlet for the waste products of combustion fromthe generator for the motive fluid utilized in the engine, so that such hot products will keep the cylinders heated to a very high degree, thereby utilizing the waste products of combustion and increasing the efficiency of the engine. By making the jackets in sections one section or part may be removed, if necessary, for cleaning without dis- .turbing the other section, and as they are not required to withstand any pressure they can be made as light castings in a convenient manner. I have herein shown and described 1n detail one practical embodiment of my invention;-

while the piston crosses the path of the abutpath, and means independent of the piston to alternately rotate and positively lock the abutment in, operative position.

4:. The combination with an annular cylinder having oppositely-located abutment-passages, and a piston to rotate in the cylinder, of a rotatably-mounted abutment, and means to rotate it intermittingly while the piston crosses the path of the abutment to enter the piston-path through one of said passages, and to leave it through the other passage."

5. The combination with a cylinder, a shaft, and an attached piston to rotate in the cylinder, of an abutment to enter the cylinder into and at right angles to the piston-path, means to lock the abutment when in such position, and means to rotate the abutment when unlocked and when the piston crosses its path and thereby move it out of and into the path a of the piston.

6. Inarotary engine, a cylinder, a piston rotatable therein, and a shaft on which the piston is mounted, combined with anabutment to close and open the piston-path, and movable at right angles thereto, and means governed by or through the shaft to intermittingly rotate the abutment and to lock it when in the piston-path.

7 In a rotary engine, a cylinder having oppositely-located passages communicating therewith, a piston rotatable in the cylinder,

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an abutment movable through said passages transversely into and out of the piston-path, a rotatable support on which the abutment is mounted and has a limited movement longitudinally thereof, and means to rotate said support intermittingly, the pressure of the motive fluid on the abutment causing the latter to seal the cylinder behind the piston during the motive action of the fluid thereupon.

8. In a rotary engine, a cylinder having oppositely 'located passages communicating therewith, a piston rotatable in the cylinder, an abutment movable through said passages transversely into and out of the piston-path, means to rotate theabutment intermittingly, the pressure of the incoming motive fluid between the piston and abutment when the latter is at rest, causing it to seal the cylinder the fluid thereupon.

9. An annular cylinder having inlet and exhaust ports on opposite sides thereof, and a passage-way intersecting the cylinder between the ports, a piston to rotate in the cylinder, an abutment, and means to rotatably move it into and out of the piston-path at right angles thereto through the passage-way and to lock it positively when in the piston-path.

10. An annular cylinder having inlet and exhaust ports on opposite sides thereof, and a passage-way intersecting the cylinder between the ports, a piston to rotate in the cylinder, an abutment, a valve to govern the admission of motive fluid through the inlet-port, and an intermittingly-rotated abutment movable into and out of the passage-way and having a lim ited lateral movement, whereby pressure of the fluid admitted to the cylinder will force the abutment against the exhaust side of the passage-way.

11. In a rotary engine, an annular cylind er,

'a rotary piston therein, a plurality of abutments movable in a path transverse to and in: tersecting the piston-path, means to move said abutments to withdraw one from and cause another one to enter into the piston-path, such withdrawal and entrance being effected just in advance of and behind the piston, respectively, and means to hold abu tments stationary when either of them is in the piston-path.

12. In a rotary engine, an annular cylinder, a rotary piston therein, a plurality of abutments rotatably-mounted to move in a path transverse to and intersecting the piston-path, each abutment when in operative position completely closing such path, means to move rotatably and intermittingly said abutments simultaneously and withdraw one from in front of the advancing piston and cause another to close its path behind it, and means to hold the abutments stationary when either of them is in the piston-path.

13. In arotary engine, an annular cylinder, a rotary piston therein, a plurality of rigidlyconnected, rotatably-mounted abutments movable in a path at right angles to and intersecting the piston-path, means to move positively and intcrmittingly said abutments to withdraw one from and to cause another to enter the piston-path, and means to lock automatically-the abutments while one of them is in position closing the piston-path.

H. In a rotary piston, an annular cylinder having inlet and exhaust ports on opposite sides, and a transverse abutment passage-way between them, a rotary piston in the cylinder, a plurality of rotatableabutments movable at right angles to the path of the piston into and out of the passage-way, and means to move positively and intermittingly, and to look when at rest, the said abutments, the withdrawal of an abutment at one side of the passage-way and the entrance of another at the opposite side being effected just before and t after, respectively, the travel of the piston across the passage-way.

15. In a rotary engine, an ammlar cylinder, a rotary piston therein, two oppositely-loeated and rotatably-mounted abutments movable in a path transverse to and intersecting the piston-path, means to lock either abutment in operative position in the cylimler, and means to intermittingly rotate the abutments when unlocked through an arc of one hundred and eighty degrees to remove one from and bring the other into and to close the piston-path.

16, In a rotary engine, an ammlar cylinder, a rotary piston therein, two op )ositely-locatml and rotatably-mounted abutmcnts movable in a path transverse to and intersecting the piston-path, means to lock either abutment in operative position in the cylinderthrough the major part of the piston-strolm, and means to withdraw one abutment from the path of the advancing piston and to move the other abutment into such path behind the piston.

17. In a rotary engine, an annular cylinder, a rotary piston therein, two connected and diametrically opposed abutments rotatably mounted to move in a circular path into and out of the piston-path, means to move one abutment out of and the other almtment into the piston-path on each pistorvstrohe, and means to loclv an abutment in operative position during the major part of the piston-st rolve.

18. In a rotary engine, an annular cylinder, a shaft, an attached piston circularly movable in the cylinder, two abutments movable alternately into and out of the piston-path, and means operatively connected with and controlled by the shaft to move one abutment into and the other abutment out of the piston-path on each piston-stroke, said means including an accelerating device to effect the movement of the abutments during only a portion of each revolution of the shaft.

19. In a rotary engine, an annular cylinder, a shaft, an attached piston circularly movable in the cylinder, two abutments movable alternately into and out-of the piston-path at right angles thereto, and means to :mtmnatically move one abutment into and the other abutment out of the piston-path on each pistonstrolve during a portion of each revolution of the shaft and to positively lock said abut ments from movement during the remainder of each shaft-revolution.

20. An annular cylinder for rotary engines, comprising opposed halves each having a circular groove in its inner face concentric with the piston-path, a shaft extended transversely through the cylinder and coaxial with said grooves, a piston-dish secured to the shaft and having an attached piston movable in the cylinder, an annular packing-carrier in each groove, means to conduct lluid under pressure into the grooves to act upon and maintain each carrier in yielding contact with the adjacent face of the disk, and packing-rings on the outer and inner peripheries of each carrier .in engagementwith the adjacent Walls of the grooves.

21. In a rotary engine, a cylinder, a-piston rotating therein, a shaft extended transversely through the cylinder and having an attached disk to Which the piston is secured, an abutment mounted to rotate in a path transverse to and intersecting the piston-path, a yielding shoe on the outer end of the abutment to bear against the periphery of the disk when the abutment is in operativeposition, and means to rotate intermittingl y the said" abutment.

22. In a rotary engine, a-cylinder, a piston rotating therein, a shaft extended transverely through the cylinder and having an attached disk to which the piston is secured, an abutment mounted to rotate in a path transverse to and intersecting the piston-path and hav' ing an elongated recess in its end, a yielding shoe therein to bear against the periphery of the piston-disk when the abutment'is in aperative position, and means to rotate the abutment intermittingly to withdraw it from the cylinder on the approach of the piston and to moveit into the cylinder after the piston has passed.

23. In a rotary engine, a cylinder, a piston rotatable therein, an abutment movable in a.

circular path'into and out of the cylinder, a continuously-revolving actuator movable towardand from its axis of revolution, a rotatable transmitting member operatively connected with the abutment and intermittingly engaged and moved by the actuator, and means to move the actuator relatively to its axis of revolution when in cooperation with the transmitting-member to-govern the speed of the latter. I

24;. In a rotary engine, a cylinder, a piston rotatable therein, an abutment movablein a In a rotary engine, a cylinder, a'piston rotatable therein, an abutment movable in a' circular path into and out of the cylinder, a contlnuously-revolvmg actuator movable toward and. from 1ts axis of revolution, a rotatable transmitting member operatively con nected with the abutment and intermittingly engaged and moved by the actuator, means to move the actuator relatively to its axis of revolution when in cooperation with the transmitting member,'to accelerate the speed of the latter, and a rotating locking device to cooperate with the transmitting member in alternation withthe actuator, to lock saidmember between 1ts successive movements.

26. In arotary engine, a-cylinder, a piston rotatable therein, an abutment movable in a circular path into and out of the cylinder, an actuator continuously revolving at a predetermined rate relative to the piston and movable toward and from its axis of revolution, a rotatable transmitting member operatively connected with the abutment and rotated step by step by intermittingengagement with the actuator, and means to move the latter relatively to its axis of revolution when cooperating with the transmitting member, to accelerate the speed thereof.

27 In a rotary engine, a cylinder, a piston rotatable therein, an-abutment movable in a circular path into and out of the cylinder, a continuously-revolving actuator movable toward and from its axis of revolution, a radially-slotted, rotatable transmitting member operativelyconnected with the abutment and intermittingly moved by the entrance into and departure of the actuator from the slots, and means to movethe actuator away from its axis of revolution while cooperating with and a cam having a circular portion and sym metrical high portions, to govern the movement of the actuator relative to its axis of revolution, said actuator entering and'leaving a slot-of the transmitting member at the high portions when the slot is tangential to the circular portion of the cam, a straight portion of the cam between the high points governing the actuator betweenthem.

i 29. In a rotary engine, a cylinder, a piston rotatabletherein, an abutment movable in a circular path into and outof the cylinder, a continuously-revolving actuator movable to- Ward and from its axis of revolution, a radially-slotted, rotatable transmitting member operatively connected with the abutment and intermittingly moved by the entrance into and departure of the actuator from the slots, and a cam having a circular portion, and tangent portions in planes intersecting the axis of rotation of the transmitting member, the extremities of the tangent portions being connected by a straight portion, the tangent portions moving the'actuator into and out of the radial slots ofthe transmitting member without jarring and causing the speed of said member to be accelerated during the engagement therewith by the actuator.

30. In a rotary engine, a cylinder, a piston rotatable therein, an abutment movable in a circular path into and out of the cylinder, at continuously-rotating shaft having a radial arm, an actuator carried by the arm and movable toward and from said shaft in parallelism therewith, a rotatable, radially-slotted disk operatively connected with the abutment and located at one side of the path of said arm, the actuator moving into and out of a slot on each revolution of the shaft and partly rot-ating the disk, and a cam on the opposite side of the path of said arm and in eligagement with the actuator, to govern its entrance to and exit from a slot of the disk and direct its movement during cooperation with the disk, to control the speed of angular movement of the latter.

31. In a rotary engine, a cylinder, a piston rotatable therein, an abutment movable in a circular path into and out of the cylinder, a continuously-rotating shaft having a radial arm, an actuator carried by the arm and movable toward and from said shaftin parallelism therewith, a rotatable, radially-slotted disk operatively connected with the abutment and located at one side of the path of said arm, the actuator moving into and out of a slot on each revolution of the shaft and partly rotating the disk, a cam to cooperate with the actuator and vary its 'adial movement when in engagement with the disk, and an intermittingly-operating locking device to cooperate with the disk and hold it from movement when the actuator is disengaged therefrom.

32. In a rotary engine, a cylinder, a piston rotatable therein, an abutment movable in a circular path into and out of the cylinder, a continuously-rotating shaft having a radial arm, an actuator carried by the arm and movable toward and from said shaft in parallelism therewith, alocking-segment on the shaft, a rotatable, radially-slotted disk operatively connected with the abutment and adapted to be intermittingly engaged by the actuator, said disk having peripheral concave seats between the slots to cooperate with the lockingsegment, the actuator moving into and out of a slot on each revolution of the shaft, to partially rotate the disk, and a cam to cooperate with the actuator and vary its *adial movement when in engagement with the disk, to control the speed of angular movement of the latter.

33. In a rotary engine, a cylinder, a main shaft extended transversely through it, a piston secured to the shaft and rotatable in the cylinder, two diametrically opposite abutments rotatably mounted and movable in a circular pathinto and out of the piston, acontinuously-revolving actuator operatively connected with and drivcnby the main shaft and movable toward and from its own axis of revolution, a rotatable transmitting member operatively connected with the abutments and intermittingly engaged and moved by t'heactuator, and n Bansto move the latter relatively to its axis of revolution when in cooperation with the t'li'ansmitting member, to govern the speed of the latter, each forward movement of the transmittingmember movingone abutment out of and the other abutment into the path of the piston, before and behind thelatter respectively.

3t. vIn a rotary engine, a cylinder, a main shaft extended transversely through it, a piston secured to the shaft and rotatable in the cylinder, two diametrically opposite abutments rotatably mounted and movable in a circular path intoand outof the piston, a contimiously-revolving actuator moval do toward and from itsaxisof revolution and positively driven by the main shaft at a 1n'edeterminml rate relatively thereto, a rotatable transmitting member operatively connected with the abutments, and intermittingly engaged and moved by the actuator, means to loch said member between its intermitting movements, and a cam to move the actuator relatively to its axis of revolution when eoi'iperating with the transmitting member, to govern the speed of the latter.

35. ln a rotary engine, a cylinder, :1 piston rotatabletherein, a main shaft extended transversely through the cylinder and to which the piston is attached,twoconnected and diametrically opposite abutments movable in a ellcular path into and out of the cylinder in the path of the piston, a counter-shaft positively driven by the main shaft, a lockirig-segment and an actuator mounted on said countershaft, the actuator being movable toward and from the counter-shaft. a radially-slot ted starwheel adapted to be intermittingly engaged and moved by the actuatt and provided with peripheral concave seats to succe sively cooperate with the locking-segment, said starwheel being operatively connected with and adapted to rotate intermittingly the abut ments, and an accelerating device to cooperate with the actuator and move it radially to increase the rapidity of movement of the starwhecl when said actuattn is in operative engagement therewith, each movement of the star-wheel moving on abutment out of the cylinder and the other abutment thereinto to permit the piston to travel across the abutment-path.

56. In a rotary engine, high and low pressure annular cylinders, a main shaft extended through them, pistons rotatable in the cylinders and secured to the main shaftdiametrically opposite each other, a rotatabl abutment for each cylinder, movable in a circular path intersecting the piston-path in each, and connections between the main sha ft and each abutment to impart intermittent rotative movement thereto, to cause the said abutments to shaft to alternately lock and rotatably move the abutments, the movement of each abutment carrying it out of'the cylinder in advance of, and causing it to enter the cylinder behind, its piston, to permit the latter to cross the path of movement of the abutment.

88. In a rotary engine, high and low pressure annular cylinders provided with inlet and exhaust ports, a main shaft extending through the centers of the cylinders, pistons rotatable in the latter and secured to the shaft diametrically opposite each other, a rotatable valve controlling the admission of motive fluid to the inlet-port of the high-pressure cylinder, an abutment for each cylinder, movable in a circular path intersecting the piston-path thereof, means actuated by the main shaft to move the abutments into their cylinders at one side and from the cylinders at the opposite side, a connection between the exhaust-port of the high-pressure cylinder and the inlet of the low-pressure cylinder, and means on the piston of the latter to govern the inlet and exhaust ports of the low-pressure cylinder.

39. In a rotary engine, high and low pressure annular cylinders provided with inlet and exhaust ports, a main shaft'extending through the centers of the cylinders, pistons rotatable in the latter and secured tothe shaft diametrically opposite each other, a rotatable valve controlling the admission of motive fluid to the inlet-port'of the high-pressure cylinder, two rotatably-mounted and diametrically opposite abutments for each cylinder, movable in a circular path intersecting the cylinder, intermittingly-operating means actuated by the main shaft to move one abutment of each pair out of its cylinder in front of the piston and to move the other abutment into the cylinder after the piston has moved past, a connection between the exhaust-port of the high-pressure cylinder and the inlet-port of the low-pressure cylinder, and means to govern the inlet and exhaust ports of the low-pressure cylinder.

40. In a rotary engine, high and low pressure annular cylinders provided with inlet and exhaust ports, a main shaft extending through the centers of the cylinders, pistons rotatable in the latter and secured to the shaft diametrically opposite each other, separate means to control the inlet and exhaust ports of the two cylinders, aconnection between the exhaustabutments to cooperate with and movablein a circular path intersecting each cylinder, means to intermittingly move the pairs of abutments to move one of each pair out of the path of its piston and the other into the cylinder behind the piston, andmeans to lock the abutments in operative position in the cylinders.

[4:1. In a rotary engine, high and low pressure annular cylinders provided with inlet and exhaust ports, a main shaft extending through the centers of the cylinders, pistons rotatable in the latter and secured to the shaft diametrically opposite each other, a rotatable valve controlling the admission of motive fluid to the inlet-port of the high-pressure cylinder, two rotatablymounted and diametrically opposite abutments for each cylinder, movable in a circular path intersecting the cylinder, intermittinglyoperating means actuated by the main shaft to move one abutment of each pair out of its cylinder in front of the piston and to movethe other abutment into the cylinder after the piston has moved past, a connection between the exhaust-port of the highpressure cylinder and the inlet-port of the low-pressure cylinder, extensions on the lowpressure piston to govern the ports thereof at each revolution of the piston, a device to accelerate the movement of the abutments cooperating with the high-pressure piston, and meansto retard the movement of the lowpressure abutments to accommodate the greater length of the low-pressure piston.

42. In a compound rotary engine, high and low pressure annular cylinders, a piston rotatable in each, packing-rings on the pistons, a valve to control the admission ofv motive fluid to the high-pressure cylinder, a connecable abutments movable into and out of the cylinders.

43. In acompound rotary engine, a lowpressure cylinder having inlet and exhaust ports on opposite sides and between them a transverse passage-way intersecting the piston-path, an abutment movable into and out of the passage-way, a piston rotatable in the cylinder, and extensions on opposite ends of the piston to cooperate respectively with the inlet and exhaustv ports, the latter being closed when the abutment is moved out of the cylinder in front of the'advancing piston, thereby preventing admitted motive fluid to pass at such time direct tothe exhaust.

44:. In a compoundrotary engine, a lowpressure cylinder having inlet and exhaust ports on opposite walls of the piston-chamber and provided with a transverse passage-way intersecting the piston-path between the ports,

an abutment movable into and out of the passage-Way, a piston rotatable in the cylinder, and externally-convex extensions on the ends of the piston adapted to contact with opposite Walls of the piston-chamber, the leading extension and the piston-body closing the exhaust when the abutment is withdrawn to permit'the passing of the piston while the follo-wing extension prevents opening of the exhaust before the inlet has been closed by the leading extension.

45. In a rotary engine, an annular cylinder, a shaft extended through it and having a disk fast thereon, a piston rigidly secured to the disk and traveling in the cylinder, said piston having annular grooves, expansible packingrings mounted in said grooves, the ends of the rings being notched and separated by the disk, and locking-lugs in the grooves to enter the notches and position the free ends of the rings, the latter bearing against the circular Wall of the piston-chamber.

46. In a rotary engine, a piston-disk having a peripheral extension, a piston recessed to re- ,ceive the extension and rigidly secured thereto,the piston having external annular grooves, expansible packing-rlngs seated in the grooves, the free ends of each ring receiving between them the disk extension, and auxiliary packlng means on the dlsk to prevent leakage of motive fluid at the ends of the pack ing-rings.

47. In a rotary compound engine, a main shaft, high and low pressure annular cylinders concentric therewith, each having a transverse abutment passage-way, pistons rotatal )lQ in the cylinders and secured to the shaft diametrically opposite each other, a rotatable abutment to cooperate with each cylinder, :1 fluid-tight casing for each abutment, the abutment passage-wry communicating therewith, and means actuated positively by the main shaft to intermittingly move the abutmenls for the passage of their respective pistons, the abutments moving alternately.

L8. A cylinder for rotary engines, comprising four externally-flanged sections, jacketsupporting flanges on the exterior of the sections, and a separable jacket adapted to be secured to the supporting-lianges to inclose the cylinder.

In testimony whereofl have signed my name to this specification in the presence of two sh] scribing witnesses.

\VILLIAM A. E. lllCNhlUl.

\Vitnesses:

Jonx C. Eowanos, EMILY llooous.

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