US1208875A - Rotary steam-engine. - Google Patents

Description

L. I. WING, DECD. m. w. CASTLE. ADMlNISTRATRlX.

ROTARY STEAM ENGINE. APPLICATION FILED MAY 8. 1906. RENEWED MAY 16. 1915.

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1 ,2Q8,8?5, Patented Dec. 19, 1916,

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ammmfoz L. J. WING, DECD. M. w. CASTLE. ADMINISTRATRIX. ROTARY STEAM ENGINE. APPLICATION FILED MAY 8. 1906. RENEWED MAY 16. I916.

1,208,875. Patented Dec.19,1916.

7 SHEETSSHEET 3- L. J. WING, DECD. M w CASTLE ADMINISTRATRIX ROTARY STEAM ENGINE. APPLICATION FILED MAY8,1906- RENEWED MAY 16,1916.

Patented Dec. 19, 1916.

YSHEETS-SHEET 4- witnesses 0 v L. J. WING, DECD. M w CASTLE. ADMINISTRATRIX ROTARY STEAM ENGINE.

APPLICATION mm MAY. 8, 190m RENEWED MAY I6. 1916.

Patented Dec. 19,1916.

YHL' meals PEYERs L0,. womumo wAswnc mu c L. J. WING, DECD. M. w. CASTLE. ADMINISTRATRIX. ROTARY STEAM ENGINE. APPLICATION FILED MAY a. 1906. RENEWED MAY 16. I9l6.

l 208,875. Patented Dec. 19, 1916.

1SHEETSSHEET 6.

W da Wy 1m: NORRIS PEYERS c0. Puoroumm. wAsnlNGmM, D. L

L. J. WING, DECD- m. w. CASTLE. ADMINISTRATRIX. ROTARY STEAM ENGINE. APPLICATION FILED MAYB, 1906. RENEWED MAY 16.1916.

'75 Patented Dec. 19, 1916.

TSHEETSSHEET 7- wuwfo c leans/er Wihwooeo rinrrnn srarns earner orrrcn LEANDER J. WING, OF LEXINGTON, MASSACHUSETTS; MABEL "WING CASTLE, OF

LEXINGTON, MASSACHUSETTS, ADMINISTRATRIX DECEASED.

OF SAID LEANDER J. VIING,

ROTARY STEAM-ENGINE.

Application filed May 8, 1906, Serial No. 315,803. Renewed May 16, 1916.

To all whom it may concern:

Be it known that I, LEANDER J. WING, a citizen of the United States, residing at Lexington, in the county of Middlesex and State of Massachusetts, have invented certain new and useful Improvements in Rotary Steam-Engines, of.which the following is a specification.

My invention relates toan improvement in rotary steam engines, of the annular and concentric type ofcylinder, through which a piston revolves carrying the main shaft with it, the bore of the cylinder being circular in cross section, the piston being provided with self expanding packing rings, and the engine being further provided with a revolving disk abutment, balanced and counterweighted and adapted to revolve at right angles across the piston path at a uniform speed with the piston, with facilities for automatic cut off and expansion of steam, to insure the highest attainable degree of economy in fuel.

Designers and builders of the better type of the reciprocating piston engine, have for some time realized the need of a higher piston speed, in order to secure the best possible effect of the steam and also to increase the efficiency of their engines, without increasing the weight of metal composing them, or the cost of their production. The attempt to satisfactorily solve this problem, has resulted in securing a much greater speed of the main shaft, than was formerly deemed safe or practicable, and has also involved many new problems as to steam compression, balancing of parts, &c., but the limitations that stand in the way of any successful attempt to greatly increase the reciprocating movements in our most successful steam engines, are too well understood to require discussion, and it may be safely assumed that so far as a high rotative speed of the main shaft is concerned, the prudent limit has been already reached, hence it would seem that the only available way to secure the desirable results of a higher piston speed, is to replace the present reciprocating piston by a revolving piston, and thus secure the combination of a very rapid piston speed, with a moderately slow rotative speed of the main shaft.

In view of the foregoing consideration, the object of my invention is to provide Specification of Letters Patent.

Patented Dec. 19, 1916.

Serial No. 97,981.

an engine of such construction and arrangement of parts as shall secure durability in the wearing parts, through ample surfaces coming in contact, through automatic adjustment for wear, and through automatic compensation for variation in the parts in moving contact, due to the different temperatures to which said parts are subjected, under a prolonged and variable service of the engine.

A further object is to provide an engine of such construction and arrangement of parts as shall secure a flexible connection between the revolving disk abutment, and the revolving piston disk, thus avoiding any tendency to grinding or leakage, between the parts in revolving contact by reason of a variation in their expansion.

A further object is to provide an engine of such construction and arrangement of parts, as to allow the revolving disk abutment to be counterweighted or suspended over the piston disk while in operation, with the weight of the disk abutment so much reduced as to secure automatic adjustment between the two revolving parts, in spite of a variation in the expansion of said revolving parts.

A further object is to provide an engine, of such construction and arrangement of parts, as to allow the thrust of the steam within the annular cylinder, upon the abutment, to be taken upon ball hearings, in such a manner, that the proper operation of said bearings, shall in no way interfere with the flexible connection between the two revolving parts before mentioned.

In the accompanying drawings: Figure 1. is a rear elevation of the engine. Fig. 2. is an end elevation, with the valve gearing, and shafts and gears for operating the abutment removed. Fig. 3. is a cross sectional view of the engine, on a line cutting the abutment shaft in its longitudinal center, the piston being shown in elevation, with the expansible ring L. removed to show internal construction. Fig. 4. is a view in elevation of the outside of the cylinder and the abutment chamber. Fig. 5. is a view in elevation of the inside of the cylinder and the abutment chamber. Fig. 6. is a sectional view of the upper bearing for the vertical abutment shaft. Fig. 7. is a plan view of the same. Fig. 8. is an end elevation of the bearings and supporting standard for the diagonal shaft. Fig. 9. is a front elevation of the same. Fig- 10. is a view in ele vation of the inner face of the abutment ehamberrcover and rim. Fig. 11. is a side elevation of the same. Fig. 12. is a. plan view of the gland for packing the inner end of the stufling box, which packs around the elongated opening r Fig. 13. is the plan view of the gland for the outer end of the stuffing box, which packs around the shaft- D. Fig. 14:. is a plan view of the movable stufling box for the abutment siaft. Fig. 15. is a plan view showing the inner end of the abutment chamber cover, adapted to contain the flexible packing for the abut ment shaft. Fig. 16. 1s a plan new of the inner face of the suspended abutment shaft bearing. Fig. 17. 1s a plan vlew of the rear "ace of the same. Fig. 18. is a cross sectional view of the. same. Fig. 19. is an end view of the adjustable box bearing for the abutment shaft. Fig. 20. is a view in cross section of the flange for the piston. Fig. 21. is a longitudinal view of the same, in cross section. Fig. 22. is a view in elevation of the'bolt for the piston. Fig. 23. is an outline view of the split eccentric ring for the piston. Fig. 2%. is a view in outline of the outer split ring for the piston. Fig. 25. is a view in elevation of the piston disk, with outer packing rin piston extension and balancing weight in position. Fig. 26. is a view in elevation of the split meta], packing ring for the piston disk. Fig. 27. is a plan view in outline of the same. Fig. 28. is a plan view of the inner face of the expansible packing ring Fig. 29. is a seetional view of the piston arm, with the eX- pansible rings in position. Fig. 30. is a side elevation of the'piston disk complete. Fig.

31 is a plan view of the double flanged packing ring surrounding the cylinder here. Fig. 32. is an edge view of the same. Fig. 33. is a plan view of the outside of the radial ear of the piston arm, showing the devices for connecting the balancing weight with the piston rings. Fig. 34. is a plan View of the inner face of the same. Fig. 35. is an outline view, showing the connecting devices passing through the forward ear. Fig. 36. is an enlarged outline view of the adjusting device for the ball bearings and abutment. "Fig. 37. is an enlarged top view of the same. Fig. 38. is a plan view of the revolving disk abutment, showing the cut away section, and the method for coring outon the opposite side of the disk to balance the same. Fig. 39. is an enlarged plan view of a section of the grooved steel ring, showing the balls located in the groove. Fig. 10. a View in outline of the bottom of the counterbalancing yoke. Fig. 4:1.is a plan view of the balancing weight for the piston. Fig. 4:2;is an edge view of 7 (not shown) Fig. l5. is an enlarged, detached *iew in side elevation, of the stufiingbo'x for the abutment shaft. 16. is an enlarged plan View of the outer flanged end of the abutment chamber cover, showing the elongated circular opening in the center of its inner end, with the stuiimg box extending up through it.; F1 9L7. in an enlarged plan view of the ring 7". Fig. 48. is an enlarged view in side elevation of. the gland R";

In the drawings accompanying this specification, it will be seen that the main portion of the'engine' is formed of the two sections B. and B. said sections extending V vertically high enough to embrace within theircompass the'annular cylinder in their lower portion, and the abutment chamber in heir upper. The inner connecting surfaces of the sections B. and B. areformed with flanges FE. and Ff. extending-the entire length of said sections, and when the inner connecting faces of said flanges E and E are planed and scraped to a fit, they are adapted to be secured together rigidly, on a vertical line coincident with the line of the main shaft D. and at right angles to the line of the abutment shaft D. thus forming a reliable connection between the two sections B. and B. Toavoid any displacement, or lack of perfect alineinent when the two sections are detached and replaced, steady pins, slightly tapered, are put through the flanges E and E atsuitable points, which' secure perfect alinement' \Vhen thus placed 1n due position wlth each and and above mentioned base plate or foot'formed by the flanges B and B is also connected with sections B. and B; of the cylinder and abutment chamber M. by two parallel flanges E? and E whichcommencing at the outerend of the base plate or foot B and B sweep inwardly and upwardly to the center of the cylinder,-forming part of its outer shell, and thenceupwardly and outwardly to near the center of the abutment chamber, at its outer circular end, with which it connects, thus forming a substantial support for the engine at its base, and giving additional strength to the central portion of the abutment chamber, against any vibration or displacement thereof, by reason of the impact and pressure of the steam against the revolving disk abutment N. and its connecting devices, within the abutment chamber M. The parallel flanges E and E are made wide and thin, as they are only required to take the pressure in one direction, therefore they do not add greatly to the Weight ofthe engine.

In F ig. 2 it will be seen that the valve cylinders I. and I. upon the outer circle of the annular cylinder, near to its connection with the abutment chamber M. are provided with flanges I and I at each end, to which the bearings'I. and I for the valve shafts are rigidly secured. Extending from the valve cylinders I. and I. to the annular cylinder, on each side of the same, are projections, I. and I radial to the main shaft D. on the inside of which are located the steam passages E and E". which allow ingress and egress of steam to and from the bore F. of the annular cylinder. Extending outward from each side of the valve cylinders I. and I. are the flanged steam pipes I and I. which carry livesteam to, and exhaust steam from the valve cylinders I. and I. It will be further seen in Fig. 2. that at that portion of the cylinder which joins the abutment chamber M. there are formed radial projections E and E surrounding the cylinder which are adapted to contain a finished groove 0 upon the inside surrounding the bore F. fitted to hold the finished ring e which packs the abutment N. around the bore F. while similar projections E and E are adapted to contain a cavity M in which the flanges 6 and c. of the packing ring 6 are located. In the center of the abutment chamber M. between the hub sections of the annular cylinder and the top, is situated within the abutment chamber the large cavity M adapted to have the revolving disk abutment N. freely revolve therein, while on each side of this enlarged central section the abutment chamber is made on a smaller circle and is adapted to contain therein, the suspended bearings N. and N Outside of this reduced circular section the abutment chamber M. is made square, to contain within it, the box section of the suspended bearings N. and N and the adjusting devices by which the suspended bearings are kept in perfect alinement, from the outside of the abutment chamber M. Still outside of the square section just mentioned, the abutment chamber M. is finished with another circular section, flanged upon its outer end, and adapted to contain within its inner circular chamber M at one end, the packing device which allows a vertical movement of the horizontal abutment shaft D. without detriment to the proper packing of said shaft against any leakage of exhaust steam from the abutment chamber M. when the engine is in operation. This end section also furnishes a substantial support for the upper bearing (Z. for the vertical supplemental abutment shaft D while the other end of the abutment chamber is fitted with the plain cover to avoid the escape of steam from the inside of the abutment chamber M. In the center of the abutment chamber M. see Figs. 2. and I. above the smaller circular portion is formed a hollow projection m. having a flange at the top, adapted to re ceive within it the upper enlarged portion of the suspended bearings N. and N while tted to this is a gland m and m fitted to contain the adjusting screws m and m. Above this in Fig. 2. will be seen the adjusting yoke M provided with a plunger M screw threaded at the top, to compress the coil spring IV see Fig. 3. The screw threaded bolts m and m. which are secured to the upper enlarged ends of the suspended bearings N. and N after passing through the stufling boxes m and m pass through the ears M. of the yoke M and are held in position therein, by screwthreaded nuts above and below said ears, by which arrangement there is secured a flexible contact between the revolving disk abutment N. and the piston disk L. in their revolving movement across each other.

In Fig. 5. in the center of the-abutment chamber M. will be seen the circular cavity adapted to contain the disk section of the suspended bearing N. and N beyond which circular section is seen the oblong opening into which the rear part of the disk section of the suspended bearing N. and N is movably fitted. The movement being vertical, and space is allowed sufficient to cover any expansion of metals in contact, while in operation, due to maximum heat.

Figs. 16. 17. 18. and 19. show the details or. the construction of the suspended bearings N. and N and Fig. 16. shows the front face of the disk 1. with a finished steel ring a. fitted in a groove near its periphery, said steel ring being provided with a semicircular curved groove 17.. in the center of the outer face of the ring a adapted to have hardened steel balls 71.. snugly revolve therein to take the pressure of steam against the abutment In the center of the disk 92. is shown the inner end of the adjustable box 127. and a and the shaft D. by which the abutment is revolved. At the top of the disk n. is shown the enlarged projection 17.". by which it is secured to the yoke M above and below the center of the disk a are shown the screw threaded holes 01. by which it is bolted to the abutment N. when being put in position within the abutment chamber M. see Fig. 3. Fig. 17. shows the rear face of the disk n. with the shell for the box bearing in the center, outside of which are shown the small square cavities n adapted to receive the lip 29. of the adjusting lever 29. by which the bearing N. and N are put in perfect adjustment from the outside of the cylinder. Fig. 18. is a view in cross section with the box W. and a in position, and the grooved ring a shown in cross-section. Fig. 19. shows the box 02 and a looking at the smaller end.

Fig. 3. shows that the cylinder bore F. is located one-half on section B. and the other half on section 13. while the abutment N. is suspended directly over the central line which divides the two sections B. and B. and it will be seen that the thrust upon the abutment N. from the impact of the steam against it, is taken upon the ball bearings 11 a. partly on the lower side of the shaft, where the pressure coincides with the direction of the steam pressure upon the abutment N. while the action is just the reverse upon the upper side of the shaft, therefore it seems desirable that the curved groove a. should be on as large a circle as possible, to keep the maximum pressure upon the balls as small as possible.

Figs. 35. and 36. show, mostly in outline, the device for adjusting the suspended bear ings N. and N in their contact with the balls, and through these with the revolving disk abutment N. and the device consists of four substantial levers, 79. located on each side of the abutment, said levers p. 79. having a large hole near one end, and the other end formed with a lip 79. at one side to engage the hole a. in the rear face of the suspended bearing N. and N in such a manner as to cause the lever 79. to be moved vertically when the bearing N. and N is so moved and to the same extent.

In Fig. 5. at each side of the central opening in the abutment chamber 2. are shown two deep narrow pockets 8. 8. one above the other, with a cored cavity between, said pockets 8. .9. adapted to contain loosely the levers p. 79. and to be movably supported therein. Near the end or bottom of the pockets .9. s. a circular opening 9. q. is cut through the metal intervening between the pockets 8. s. and the outside, and a like hole somewhat smaller in diameter is cut through from said pocket 8. s. to the central opening in which the box bearing is located to allow of the introduction therein of a tightly fitting eccentric pin 1. see Figs. 36. and 37. by which a. fine adjustment is imparted to the position of the suspended bearings N. andN and the abutment N. The flanged. pin P. is finished in such a manner that the inner end 72 shall be on the same plane with the outer end 29 although ofsmaller diameter, while the central portion 27*. is made eccentric to both, and is adapted to nicely fit within theopenings in the lever 29. The

pin P. is further provided with a flange 39.

finished on both sides, with semicircular grooves 72 p extending nearly around it, adapted to have threaded tap bolts 79. 10- pass through said grooves and secure the flanges rigidly in any desired position, while in the center of the flange is a square cavity 39 adapted to have fitted therein the end of a wrench, by which the pin P. may be oscillated in either direction, when the tap bolts 79. p. are loosened and the packing eneath the flange permits. In this manner a perfect adjustment of the internal and movable members is easily accomplished.

In Fig. 3. it will be seen that long bolts of small size, with heads, are passed through the ears n. of the box bearings a and a and through holes in the disk of the suspended bearing N. and N and are tightly screwed into the hub portion of the revolving abutment N. for two purposes, first to hold the different parts in proper position when they are placed within the abutment chamber M. All of the parts being assembled are placed in position together, and when the two sections B. and B. of the cylinder are rigidly. secured together by means of their connecting flanges E and E the long bolts are removed and short bolts of larger size adapted to pass freely through the ears of the gland n. and engage screw threaded holes it. in the box bearing a and a by which the position of the gland 7 a. is adjusted, all of which is done from the outer end of the abutment chamber M. when the covers R. and R. are removed. A second reason for inserting the long bolts in the position hereinbefore mentioned, is to enable the curved steel rings to be tightly held against the balls which revolve in the grooves of said steel rings and'fill said grooves, thus bringing the balls and grooves into perfect alinement, so that when the tapered glands of box bearings 92*. and a are placed in position within the box a. these glands may be babbitted and thus the ball a. the groove WP. and the abutment shaft D. and the tapered gland will all be brought into perfect alinement before they are put into their respective operative positions. It will thus be seen that the revolving abutment N. the abutment shaft D. the suspended bearings N. and N with the box bearings M. and m. are all held in suspension within the abutment chamber M. and are adapted to allow such vertical movement of these parts as may be necessary to maintain a flexible contact between the abutment less degree of heat to which they are exposed, under the varying conditions which the engine is called upon to work in the service required of it. It will be remembered that only such a proportion of the weight of the abutment N. and its connections is allowed to bear upon the piston disk L. as shall be found necessary to secure a good wearing contact between these parts, and this is easily regulated by the proper manipulation of the screw threaded plunger M. at the top of the engine.

The abutment chamber cover R. for section B. of the engine is shown in cross section, in due position, in Fig. 3. and in end and side elevations in Figs. 10. and 11. and consists of a short plain cylinder, having a head r. at one end, and is formed with an outwardly extending flange 1". on the other end, by which, when said flange r. is finished to fit therein, it is secured to the outer end of the abutment chamber M. by screw threaded tap bolts 1. passing through the flange r. into and through the flange m formed upon the outer end of the abutment chamber M. and rigidly securing it thereto, its purpose being simplyto close that end of the abutment chamber M. against any leakage of the exhaust steam from within the abutment chamber, it being also easily removed, to admit of any desired adjustment of the box bearings a and a at that end of the abutment shaft D. from the outside.

The abutment chamber cover R. is shown in position, in cross section, in Fig. 3, and is like the cover R. just described, except that in the closed end 1 seen in Fig. 10. there is an elongated circular opening W. in the cover R. and upon each side of this opening are parallel projections W. and r extending outward, the inner edges of which and the space between are fitted to receive the upper finished face 7- of the flange r. of the stufiing box R which flange T is adapted to have a vertical movement betwen the parallel projections 1". and 1*". when the abutment shaft D. is moved vertically by reason of the expansion of the abutment N. and'the piston disk L. The stuffing box R is formed with two glands Fig. 13. and R Fig. 12, both fitted to a screw threaded contact with the outside of the stuffing box R The gland R. is adapted to pack the elongated opening r against any leakage of exhaust steam around the out side of the stuffing box R while the gland R is fitted to pack around the shaft D. inside the stuffing box R and is screw threaded upon its outer ring to engage the screw threads onthe outside of the stuffing box R The inside bottom of the cover R. is finished to allow the gland R to fit tightly thereon.

The revolving disk abutment N. is shown in cross :SfiQfiQIl, in due position in Fig. 3.

and a plan view in outline is shown in Fig. 38. and it consists of a substantial disk pro vided with a wide short hub N in its cen ter, one half on each side of the disk, with an opening in the center to allow the abutment shaft D. to be firmly secured therein by a substantial feather, or other desirable means. At one side of the disk it is cut away to allow the piston G. to freely pass through it, when the piston G. and the abutment N. are in motion. The cut-away section N is large enough to allow not only the piston rings G. and G to pass it freely but also to allow the balancing weight L and the piston extension L to do the same. side of the shaft D. from the cut-away section B in the plate of the disk N. the metal is cored away upon the inside of the plate leaving a thickness of metal on each face of the plate suflicient to withstand the steam pressure upon the outside of the plate, when the pressure is at its maximum without bending or breaking under the strain, and to assist the reduced plates in sustaining said pressure substantial studs h. h. h. are left in the cored part, the area so cored out being sutlicient to offset the metal cored out of the plate and provide a means of balancing the abutment when in motion. The outer periphery of the disk is finished in a curve to fit the curve of the piston disk L. so that the area of contact between the piston disk L. and the abutment N. shall in one direction equal the thickness of the abutment, and in the other direction the thickness of the piston disk, thus giving a very substantial surface for contact of the wearing parts. The broad hub if. of the abutment- N. is provided with the same appliances for containing the balls as are to be seen in the front face of the suspended bearings N. and N being a groove N finished in the hub a near its outer edge, and adapted to contain the grooved steel ring in which the balls are located, seen on an enlarged scale in Fig. 39. By a careful study of the devices for adjusting the contact of the balls on each side of the hub 71*. of the abutment N. it will be seen that the whole pressure and impact of the steam against the abutment N. is taken upon the balls a and in such a manner as in no wise to interfere with any small vertical movement of the abutment N. by reason of any unusual expansion of the metals in moving contact, within the abutment chamber M.

In Fig. 5. there is shown a circular groove 0 surrounding the bore F. adapted to have nicely fitted therein, the lower portion 6. of the double flanged packing ring 6. see Figs. 31. and 32. while outside of it, and surrounding the groove O is located a chamber M adapted to loosely contain the flanges 6 and 6 of the double flanged packing ring 6. which packs the abutment N. around the bore F. Near the outer end of the flanges On the opposite c and a are located holes 6. and 6 through the flanges 6 and 0 adapted to receive therein, small bolts with square counter sunk heads, having check nut-s on the other side of the flanges 6 and to hold the bolts in place with springs (not shown) for holding the flanges c and 0 in contact with the abutment N. and outer chuck nuts, also not shown, on said bolts to control the position of the packing flanges c and e. from the outside of the cylinder.

In Fig. 25. is shown the piston disk L. complete, with the piston extension L the outer piston packing ring G. and the balancing weight L. in position, with the piston arm L shown in dotted lines beneath the expansible packing ring L". In Fig. 2. these same parts are shown, except the outer expansible packing 'ring L". which is removed to show the construction of the inner ring L and how the piston arm L is made to pass through it. The periphery of the expansible packing ring L of which there are two, is formed with inter-locking segments, and beneath these segments is finished a deep groove L adapted to snugly contain the soft metal split packing ring L. see Figs. 26. and 27. while beneath this groove L. are made pocket-s L adapted to contain steel coil springs (not shown) to press the packing rings L outwardly, and compensate for the wear upon its outer side surface. The split ring L being made of softer metal than the parts surrounding it, is more expa-nsible under heat, and while its temperature is normal, it snugly fills the groove L but not so tightly as to interfere with the outward pressure of the springs located in the pockets L As soon as steam is introduced into the bore F. the greater expansibility of the ring L causes it to fill the groove L so full as tohold the rings L in a rigid position, as to any outward expansion, by which it will be seen that every time the cylinder of the engine cools off, this device will automatically take up the wear on the piston disk L. in its contact with the inner surfaces of the piston disk cavity F Figs. 3. 25. and 29. show that the outer end of the piston arm L is provided with outwardly extending radial ears L. and L between the finished parallel faces of which are located the self expanding packing rings G.

and G which with the ears L. and L form the piston G. In the center of the ears L.

and L is shown a hole Z. see Figs. 29. 33. 3d. and 35. adapted to receive snugly the bolt Q. Fig. 22. while the flanged ring L Figs. 20. and 21. is fitted to fill the space between the parallel faces of the ears L. and L around the center, and inclosing the bolt Q. which is of such length that when the flanged ring is in position, the bolt Q. will hold the parallel faces of the ears L. and L rigidly against the ends of the Iflanged and L radially or otherwise, and still remain steam tight, on account OfWlllCli freedom of movement, when the piston is rapidly revolved within the cylinder, the ring G. and G will be liable to the effect of centrifugal force to such an extent as will wear the ring G. of the piston, G. or the bore F.

of the cylinder more on the outer than the inside, and to counteract this effect, a balancing weight L is secured to the ear L upon the outside of which is formed a radial projection having beveled sides which the weight L is adapted to fit upon having a radial movement thereon. By this arrangement the rings G. and G of the'piston G. and the balancing weight, because they contain the same amount of metal, are subjected to the same degree of centrifugal force, hence if they are connected with each other by a bailancing lever, in a propermanner, one will counterbalance the other, at whateverspeed they may be revolving.

It seems desirable that the device for connecting the rings G. and G with the balancing weight L should be such as to admit of the steam being applied to either side P of the revolving piston G. at will, and proper care should be taken to prevent the passage.

of live steam inside of the piston rings, G. and G whereby these rings nnght be onduly expanded, while in operation, creating undue friction between the outside surface of the ring G. and the inner finished surface of the bore F. To prevent this the radial ear L is formed with alarger open,-

ing through it, beneath the opening Z. for' the bolt Q. and this opening Z jis screwthreaded to admit of the introduction there in, ofa flanged bushing Z. being tightly screw-threaded therein, from the outside,

the hole Z in the bushing Z. is adapted to receive therein, the headed spindle Zt as' far as the shoulder on said spindle will permit, while the head of the spindle ZHis turned at right angles to adapt it to bear upon the bottom part of the ring G see Fig. 3%. The outer end of the spindle Z. is adapted to have fitted thereto, a small elongated cap Z Fig. 33. having the same leverage from the center of the spindle Z asthe head of the same; When the weight L". is placed in position over the projection having beveled sides to keep it in place, it is of such form as to cover the small cap Z without binding, and by inserting the screw-threaded pin Z. through the weight so that it will be pressed by the outer end of the elongated cap Z. the device is made complete. In Figs. 8. and 9. will be seen the standard and hearing B. for the diagonal shaft D which connefits the main shaft with the vertical supplemental abutment shaft D The finely adjustable main bearings B. are shown in Fig. 1.

In this engine the valves, and the devices for operating them are thesame as those shown in my application filed April :27. 1904. Serial Number 205.169.

It will be understood that the abutment N. shown in these drawings is finished upon both faces, and is therefore adapted to revolve in either direction in accordance with whichever side of the piston the steam pres sure is applied. In an engine designed to revolve in out one direction the inside coring of the disk may be dispensed with, and the metal can be taken from the disk opposite the cut away section upon the under side of the same, to balance the abutment, and the second finished face may be omitted.

The abutment N. is caused to revolve at a uniform speed with the piston and main shaft D. by the use of the following gears: Secured to the main shaft D. near the inner end of the main bearing C. is a bevel gear which impinges a like bevel. gear H. which is secured to the adjacent end of the diagonal shaft D and actuates the same, while the other end of the" shaft D is pro vided with a miter gear H adapted to connect with and revolve a like miter gear H secured to the lower end of the vertical supplemental abutment shaft D to which shaft at its upper end is secured a like miter gear H adapted to impinge and operate the like gear H secured to the horizontal abutment shaft D. and since the gears are of uniform diameter the rotation of the piston and main shaft will be identical with the abutment shaft.

In Fig. 40. will be seen view of the lower ended the yoke M showing its beveled connections with the projections on each side of the abutment chamber, by which any twisting of the yoke h is avoided.

Figs. 41. and 42. show the method by which the balancing weight L is secured to the ear L in such a manner as to give it any desired radial movement.

In Figs. 33. and'S-f. it will be observed that the head of the spindle 5*. extends in an opposite direction for the elongated cap Z in order that a like pressure upon either may counterbalance the other.

Figs. 4-1. to 48. inclusive, are enlarged, detached views to more fully show the construction of the device for packing the abut ment shaft D. where it passes through the abutment chamber cover R. Just above the an outline plan flange r. of the stufling box E on the outside thereof is formed a shoulder T of a height corresponding with the thickness of the finished inner head 7'. of the abutment chamber cover R. which shoulder furnishes a substantial seat for the ring 9*. to rest upon, and also prevents the ring r. from being too rigidly pressed against the inside finished face of the head r. of the abutment chamber cover B. when the gland R is et in proper position to pack the connecting surfaces. The ring T is sufiicicntly large in diameter to cover the elongated circular opening 1. in the head 1*. and lap sufficiently over its sides to cover any vertical movement of the shaft D. and stuffing box R due to the expansion of the abutment N. and the piston disk L. when in operation. By this arrangement it will be seen that the same packing which packs around the stufiing box R where the ring 1*. is tightly fitted, also packs around the outer edge of the ring 9". against any leakage of the exhaust steam from the abutment chamber M. and in no wise interferes with the vertical movement of the abutment shaft D. The movement being small the packing so arranged should have great durability, with need of adjustment at hing intervals of time.

In Fig. No. 31 T have shown the packing plate which is "apted to be pressed against the outer flat surfaces of the dish-aluitment by springs (not shown) located in the adjacent metal of the cylinder. Said springs are adjustable from the outside. This plate is adapted to fit into a groove surrounding the base within the abutment chamber and is provided with a hole in the center through which the piston passes; its form is somewhat segmental. The purpose of the segmental form is to provide a wearing surface, which rests upon the outer parallel face of the disk-abutment and is of such form as to qualize the wear between them, by increasing the area of the packing plate to a. de gree corresponding with the increased speed of the surface of the abutment-disk as its periphery is approached. There are three elements which enter into this problem: The varying of the speed of the surface of the disk and pressure. Now as the speed and pressure are fixed the wear must be equalized by a change in the area of one or more of the parts in moving contact and the desired effect is best reached by a modification of the form of the wearing surface of the pack ing plate; this form is shown in Fig. 3. My method of balancing the rotating diskabut ment consists in removing some of the metal flat side of the disk, but always within the periphery so that a wearing surface is always left at and near the periphery, enough being taken out to balance the cutaway part of the disk-abutment. This I term internally balancing the disk.

Having fully described my invention, what I claim as new and desire to secure by Letters Patent is 1. A rotary steam engine having an annular cylinder, with a continuous finished shafts of the piston disk and abutment,

whereby they shall revolve at a relative, uniform, rotative speed, means for malntaining a flexible connection between the piston disk .and abutment, means connected with the abutment for taking the impact and pressure of the steam against the abutment upon ball bearings, with internal devices for automatic compensation for wear and expansion in the moving parts in contact,together with means for automatic cut-off and expansion of the steam within the cylinder, substantially as shown and described, and for the purposes herein set forth.

2. In a rotary engine, the combination with the cylinder, provided with a single steam inlet, and a single exhaust outlet, of a revolving disk abutment, internally balanced and counter-poised located between said inlet and exhaust openings, and a revolving piston rotatable within said cylinder, substantially as shown and described, and for the purposes herein set forth. 7

3. In a rotary engine, a revolving disk abutment, internally balanced and counterpoised, said abutment having a cut-away section at one side of its central hub, with means for revolving said disk at right angles across the bore of the cylinder and across the piston disk, substantially as shown and described, and for the purposes herein set forth.

4. In a. rotary engine, the combination with the annular cylinder, having a bore that is circular in cross section, a revolving disk adapted to carry a piston around said bore, a balanced and counter-poised disk abutment, having a cut-away section on one side of said disk, of a deep circular chamber adapted to contain said disk abutment, arranged to cut across the bore of the cylinder at right angles, said abutment adapted to revolve freely in either direction across the piston path, substantially as shown and described, and for the purposes herein set forth.

5. In a rotary engine, the combination with the annular cylinder, the revolving piston disk carrying a piston, of a balanced and counter-poised disk abutment, the disk being finished on both surfaces, and adapted to be packed on one or both of said surfaces, and provided with a cut-away section in said disk and having a curved outer edge to snugly fit against the periphery of the piston forth.

disk across which it revolves, substantially as shown and described, and for the purposes herein set forth.

6. In a rotary engine, the combination with the cylinder, the'revolving piston disk, and the balanced and counter-poised abutment, having acut-away section in said disk, and with one or more finished faces adapted to be packed, of a split metal ring located in a groove around the cylinder bore, said ring being formed with outwardly ex tending flanges on each side at the top of said ring, said flanges finished to pack against the finished faces of the disk, and being provided with springs beneath said flanges to hold it in easy contact with the same, substantially as shown and described, and for the purposes herein set forth.

7. In a rotary engine, an internally balanced and counter-poised disk abutment with a cut-away section on one side of the disk, substantially as shown and described, and for the purposes herein set forth.

disk

8. In a rotary engine, the combination" with the revolving piston disk, a piston located between radially extending ears there on, a balancing weight secured to one ear, of a balancing spindle, fulcrumed in a flanged bushing rigidly fixed in the center of said ear said spindle having a head turned at right angles within the piston rings and an elongated cap secured to the other end, the former engaging the inside bottom of the inner piston ring, and the latter engaging the balancing weight, in such a manner that the centrifugal force exerted on the rings will be offset by a like force exerted upon' the weight, substantially as shown and described, and for the purposes herein set forth.

9. In arotary engine, a revolving, balanced and counter-poised disk abutment, ar-

periphery of said abutment, and the periphery of the piston disk across which it revolves, substantially as shown and described, and for the purposes herein set 10. In a rotary engine, a balanced and counter-poised disk abutment, provided with means connected with said abutment, to insure a flexible contact between said disk and the revolving piston disk across which it moves, and devices connected with each hub of said abutment, whereby the thrust and pressure of the steam against the abutment will be taken upon ball bearings adapted to adjustably engage the hub of said disk, substantially as shown and described, and for the purposes herein set forth. 7

11 a r y gi the balanced and counter-poised disk abutment, having a cutaway section on one side of said disk, and provided with substantial hubs on each side of said disk, with enlarged diameter, to contain a groove near the periphery of said hubs, adapted to receive therein a hardened steel ring, having a curved groove in its center to which is nicely fitted the balls of the ball bearing adapted to freely revolve in said groove, with outside devices for adjusting their contact with said hubs, substantially as shown and described, and for the purposes herein set forth.

12. In a rotary engine the balanced and counter-poised disk abutment having a cutaway section on one side of said disk, with substantial hubs of enlarged diameter having devices therein adapted to receive and support the balls composing the ball bearings, of suspended abutment bearings, located within the abutment chamber on each of said enlarged hubs, said bearings fitted in their adjacent faces to support like devices for the balls as those in the hubs of said abutment, with means connected with said suspended bearings, to hold them in suspension over the bore of the cylinder and impart a flexible contact between the abutment and piston disk, substantially as shown and described, and for the purposes herein set forth.

13. In a rotary engine, the balanced and counter-poised disk abutment having a cutaway section on one side, ball bearings connected with its enlarged hubs, and suspended bearings located on each side of said disk, and adjustably connected therewith, of a double yoke having outwardly projecting ears on opposite sides, by which it is connected with the suspended bearings by means of substantial screw threaded bolts which pass through said ears and are secured there in, said yoke being provided with a plunger adapted to engage the stiff coil spring in the pocket in the top of the abutment chamber, and by means of the screw threaded contact between the plunger and yoke, any desired portion of the weight of the abutment and its connections may be taken upon the spring, substantially as shown and described, and for the purposes herein set forth.

14. A rotary engine formed of two main sections, each containing one half of the annular cylinder, and one half of the abutment chamber, the two sections being secured together through flanges formed on the inside of each section, on a vertical line coincident with the line of the main shaft, the lower portion containing the annular cylinder, and the upper portion forming the abutment chamber, each section being alike and interchange-able, the lower section being formed with a supporting base or feet, and the upper portion being adapted to contain the abutment, the abutment shaft, suspended bearings and adjusting devices for the same, with means for revolving the abutment shaft by connections with the main shaft, and at the same rotative speed, substantially as shown and described, and for the purposes herein set forth.

15. In a rotary engine, the combination with an annular cylinder, a bore therein which is circular in cross section, a revolving piston disk carrying a piston in said bore, a balanced and counter-poised disk abutment suspended above said piston disk and adapted to revolve across it at right angles, said abutment being provided with ball bearings in its hub sections, with suspended bearings located opposite the outer faces of said hubs, adapted to support said ball bearings in position, of substantial adjusting levers fitted with a curved outer end on a circle equidistant from the center of the finished hole in the other end of said levers, said levers formed with an outward extending lip at one side, adapted to engage openings in the rear face of the suspended abutment bearing and to cause the levers to move verticall when the suspended bearing moves, and to the same extent, said lever being supported in a pocket by means of an eccentric flanged pin in such a manner that any desired adjustment of the lever may be effected from the outside by partly revolving the pin in either direction, substantially as shown and described, and for the purposes herein set forth.

16. In a rotary engine the combination with an annular cylinder, having a bore that is circular in cross section, a piston disk rotatable therein carrying a piston, a balanced and counter-poised disk abutment suspended above said piston disk and adapted to revolve across the same at right angles, said abutment being provided with a shaft by which it is supported and revolved, of adjustable box bearings located in the outer portion of the suspended bearings, and adapted to be adjusted to fit the shaft, when the abutment is held in position by the ball bearings, and so arranged and adjusted that the ball bearings upon the hub of the abutment, and the box bearings upon the abutment shaft, shall work in harmony to keep the abutment and shaft in perfect alinement regardless of any vertical movement thereof, due to the expansion of the revolving parts in contact, substantially as shown and described, and for the purposes herein set forth.

1?. In rotaryengine, the combination with an annular cylinder, a bore within the same which is circular in cross-section a revolving piston disk carrying a piston, a balanced and counter-poised disk abutment, having a cutaway section on one side, a shaft rigidly secured within the center of said abutment, to support and revolve the same, within the abutment chamber, and having outward connection by gears and shafting with the main shaft by which it is revolved, of a stuffing box located near the outer reduced end of the abutment chamber, and secured to the inner end of the abutment chamber cover, upon which it has a free vertical movement, said packing box being v fitted ith two glands, having a screw-threaded connection with the outside of the stufling box, whereby one gland packs around the opening in the abutment cham ber cover, through which the stuffing box passes, and the other gland packs around the abutment shaft both allowing any desired vertical movement of the abutment shaft, substantially as shown and described, and for. the purposes herein set forth.

18. In a rotary engine, formed of two interchangeable sections secured together on a vertical line coincident with the line of the main shaft, by finished connecting faces of flanges formed upon each section, said flanges connecting at the bottom of said sections with supporting flanges formed to extend outwardly therefrom at right angles thereto, and said connecting flanges being broadened as they approach the supporting flanges, to insure a substantial base for the support of the engine, on a line coincident with the line of the main shaft, substantially as shown and described, and for the purposes herein set forth.

19. In a rotary engine, formed of two interchangeable sections, each containing one half of the annular cylinder and the abutment chamber, said abutment chamber, (when the two sections are secured together by finished connecting flanges), being adapted to contain the disk abutment with the shaft extending outside the said abutment chamber, and connecting by shafts and gears with the main shaft which actuates it, said abutment chamber being reduced in size as it extends outwardly, and being strengthcned insaid outward portion, by two parallel flanges on each section connecting at the bottom of each section with the base plate or foot and extending upward to the sides of the cylinder, of which they form a part, thence extending upward to connect with the reduced outer end of the abutment cham ber, whereby additional strength is imparted to the abutment chamber to enable it to withstand any strain upon the parts, by reason of the impact and pressure of the steam against the abutment, when in operation, substantially as shown and described, and for the purposes herein set forth.

20. In a rotary engine having a main shaft and an abutment shaft, the combination with the system of shafts and gears, connecting the main shaft with the abutment shaft, and imparting a continuous rotary motion thereto, of a combined gear casing and shaft bearing secured to the outer flange of the abutment chamber, and arranged to allow vertical movement of the shaft, without detriment to the proper operation of the connecting parts, substantially as shown and described, and for the purposes herein set forth. 7

21. In a rotary engine, a balancing yoke constructed with depending sections on opposite sides, with grooves formed upon the internal surfaces of said sections on opposite sides, with beveled sides and being adapted to slide freely upon outwardly extending project-ions located on opposite outsides of the abutment chamber, said depending sections being connected by adjustable rods with the suspended bearings which support each end of the abutment shaft, whereby each end of said shaft isgiven a uniform movement as to time, direction, and degree, substantially as shown and described, and for the purposes herein set forth.

22. In a rotary engine, a balancing yoke and plunger, a coil steel spring located in a socket formed in the upper part of the abutment chamber, and adapted to engage the lower face of said plunger, which is inserted adj ustably in and through the center of said balancing yoke, whereby the pressure of the abutment upon the piston disk, across which it revolves, is externally controlled at will, substantially as shown and described, and for the purposes herein set forth.

23. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, and a revolving piston adapted to revolve in said bore and connected by substantial devices with the main shaft, the combination of a revolving disk abutment, provided with a cut-away section in said disk near its periphery, and being internally cored out to balance against gravity and a stiff coil spring located at the top of the abutment chamber, and said abutment being suspended over the piston disk by devices that connect it with said stiff coil spring, whereby a flexible contact is maintained betweensaid disks, adapted to counteract the expansion thereof, under any increased heat to which they may be exposed, substantially as shown and described, and for the purposes herein set forth.

24. In a. rotary engine, a rotatable disk abutment having a cut away section as de' scribed upon one side of its axis of rotation, the other side of the disk having cored recessed chambers as shown, the outer finished walls over said recessed chamber, being supported by metal posts which engage each adjacent inner Wall, and adapt them to withstand the steam impact without spring or displacement, whereby'the disk is perfectly balanced, substantially as shown and described, and for the purposes herein set forth.

25. I11 a rotary engine, a rotating disk abutment having an enlarged hub, the ends of said hub having recesses for the reception of anti-friction balls, corresponding recesses made in the bearings, said bearings and anti-friction balls as described.

26. In a rotary engine, a piston carrying disk rigidly secured in position to revolve freely within the annular-cylinder, and a rotating disk abutment, pended bearings, and adapted to have its periphery revolve transversely across the periphery of the piston carrying disk, with appliances connected with said suspended bearings, whereby a yieldable contact is maintained between said revolving disks, and their expansion under heat is automatically compensated for, without detriment to the proper operation of the engine, substantially as shown and described, and for the purposes herein set forth.

In a rotary engine, a rotating disk abutment, a piston carrier rotating in a plane at right angles to the plane of the disk abutment, the peripheries of said disks running in contact, the disk abutment supported on suspended bearings over the piston carrier in such a manner as that the two disks shall be kept in close revolving contact through the force of gravity acting upon said abutment, with devices connected with said suspended bearings whereby the force of gravity is partly diverted to the stiff coil spring, and the pressure between said disks is regulated at will, as and for the purposes herein set forth.

28. In a rotary engine, a rotatable disk supported on susabutment supported upon suspended bearings, and means for automatically varying the position of said bearings and abutment, substantially as shown and described, and for the purposes herein set forth.

29. In a rotary engine, a rotatable disk abutment, and yieldable means for varying the position of said abutment, substantially as shown and described, and for the purposes herein set forth.

30. In a rotary engine, a rotating disk abutment and a piston carrier rotating in planes at right angles to each other and having their peripheries working in contact, means for yieldingly holding said peripheries in contact, whereby the changes due to expension and wear are compensated, and means for holding the said disk abutment laterally in proper position, substantially as shown and described, and for the purposes herein set forth.

31. In a rotary engine having an annular bore that is circular in cross section, a piston revoluble therein, a fiat disk abutment having smooth flat sides against which the steam abuts on either side at will, pockets formed in the metal adjacent to the revolving abutment, solid wheels occupying said pockets,

to engage the suspended bearings and hold them in exact lateral adjustment on opposite sides of said disk abutment, with outside appliances for adjusting the position of said wheels, substantially as shown and described. and for the purposes herein set forth.

32. In a rotary engine, a disk carrying a piston and a disk serving as an abutment, supported by suspended bearings, and taking the steam pressure on either flat side of said abutment, said sides being in parallel planes, the two disks adapted to rotate transversely across each other on their peripheries, means to effect automatic compensation for wear and for variation in expansion by reason of change in tempera-. ture due to varying loads carried by the engine, substantially as shown and described, and for the purposes herein set forth.

33. In a rotary engine having a rotary disk abutment rotating transversely across the piston path, and having parallel fiat finished surfaces on each side, an elongated packing adapted to fit around the outside of the cylinder bore, and means operated from the outside whereby the pressure of the packing upon the abutment is controlled at will, substantially as shown and described, and for the purposes herein set forth.

3st. In a rotary engine, having an annular cylinder the bore of which is circular in cross-section, said cylinder being provided with a cavity or circular chamber between the bore and the main shaft, in combination with a piston disk revoluble in said cavity, provided with a two part eXpansible packing ring, located on the periphery of the piston arm, with inter-looking segments formed on its curved periphery, terposed beaween its two sections that hold their outward faces against the adjacent parallel walls of the circular cavity, and a soft metal split ring located in a deep groove formed on the tions, just beneath the interlocking segments, whereby the difference in the expansion of the two metals under heat will tend to hold the expansible rings in any desired position of contact with the adjacent walls of the cavity, thereby securing automatic compensation for wear and a minimum degree of friction of the parts in contact, while in operation, substantially as shown and described, and for the purposes herein set forth.

35. In a rotary engine, having an annular bore that is circular in cross section, a piston that is rotatable therein, a piston disk cavity located between said bore and the chamber containing the hubs of the piston disk, said cavity having a finished face on each side, in combination with self-expanding rings adapted to fit snugly over the hub sections of the piston disk and joined in the center steel coiled springs ininner faces of said two secthereof by inter-locking segments provided with internal devices that hold the outer faces of said rings in revolving contact with said finished faces of the piston disk cavity, whereby the wear upon the parts in contact is automatically compensated for, substantially as shown and described, and for the purposes herein set forth.

36. In a rotary engine, having an annular bore that is circular in cross section, a piston that is rotatable therein, a piston arm, a piston disk cavity having finished walls on opposite sides thereof, self-expanding rings surrounding the piston arm and engaging the finished walls of the piston disk cavity, in combination with steel coil springs interposed between said expanding rings having interlocking segments on their periphery and adapted to press the same outwardly, and a soft metal cut ring situated in a groove beneath said interlocking segments, whereby said expanding rings are rigidly held in any desired adjustment against said finished faces of said piston disk cavity, thus effecting automatic compensation for wear between the parts in revolving contact, substantially as shown and described, and for the purposes herein set forth.

37. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a piston rotatable therein, a piston disk containing a piston arm having radial ears formed on its outer end, and constituting the heads of the piston, one or more piston rings movably secured between said heads, in combination with radial projections formed on the outside of said ears having beveled edges adapted to have movably secured thereto a balancing weight, connected by internal devices with the piston, whereby the effect of centrifugal force upon said piston is automatically neutralized, substantially as shown and described, and for the purposes herein set forth.

38. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a piston having piston rings rotatable therein, and connected with the main shaft by a piston arm having radial ears formed on its outer end with projections formed on their outsides, upon one of which cars is located a balancing weight, in combination with a balancing spindle with a head on each end and fulcrumed in one of said radial ears and adapted to engage the balancing weight at one end of the spindle, and the piston rings at the other end and to press them in opposite directions, whereby the piston is automatically freed from the effect of centrifugal force, substantially as shown and described, and for the purposes herein set forth.

39. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a piston revoluble therein with substantial connections between said piston and the main shaft, a suspended disk abutment with a flat finished face on each side of said disk and formed with a cut-away section near its periphery, in combination with a cored section of said abutment opposite said cut-away section adapted to reduce the weight of metal to equal the volume of said cut-away section, whereby the said abutment is balanced against gravity, substantially as shown and described, and for the purposes herein set forth.

40. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a piston rotatable therein and located upon the periphery of a piston disk which connects it with the main shaft, of an internally balanced abutment disk suspended over said piston disk, across which it revolves at right angles, the peripheral curve of each disk being adapted to fit snugly upon the other over the entire surface of contact, substantially as shown and described, and for the purposes herein set forth.

41. In a rotary engine, formed with an annular cylinder having a bore thatis circular in cross section, a two ring piston located between radial ears formed upon the outer end of the piston arm which connects the piston with the main shaft, said ears having radialprojections formed on their outside, in combination with a piston eXtension rigidly secured to one of said ears and revolved by said piston. whereby the clearance of the engine is reduced in volume equal to the cubic contents of said piston extension, at each revolution of the piston, substantially as shown and described, and for the purposes herein set forth. V

42. In a rotary engine, formed with an annular cylinder and having a bore that is circular in cross section, a revoluble piston disk carrying a piston and connecting. the same with the main shaft, a disk abutment yieldably suspended over said piston disk, and adapted to revolve across the same at right angles thereto, in combination with main shaft bearings formed with devices that allow of their vertical adj ustment,without other displacement, substantially as ring will engage the hither end of the cylinder bore, before the other side of said outer whereby one side of the said outer piston Y substantially as piston ring leaves the thither end of the cylinder bore, the piston is adapted to pass over said slot freely without ar or displacement, substantially as shown and described, and for the purposes herein set forth.

44:. In a rotary engine, formed with an annular cylinder having a bore that is circular in cross section, a two ring piston carried by a piston arm rotatable in said bore, of a piston disk connecting said piston with the main shaft, said disk being formed by expansible interlocking rings located upon the hub sections of the piston arm and covering the same, substantially as shown and described, and for the purposes herein set forth.

45. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a piston that is rotatable thereinlocated between radial ears formed on the outer end of a piston arm, in combination with a double flanged ring secured between said ears, and a self expanding piston inclosing said double flanged ring, substantially as shown and described, and for the purposes herein set forth.

46. In a rotary engine, having an annular cylinder provided with a bore that is circular in cross section, a revolving piston carried by a piston disk having radial ears formed on its periphery, said ears having finished parallel faces, a double flanged ring secured between said ears and a two ring piston encircling said ring, of a single bolt for securing said parts against displacement, shown and described, and for the purposes herein set forth.

47. In a rotary engine, having an annular cylinder with a bore that is circular in cross section, a self-expanding piston rotatable therein, in combination with a yieldable, rotatable, and balanced disk abutment, substantially as shown and described, and for the purposes herein set forth.

In a rotary engine, having an annular cylinder provided with a bore that is circular in cross-section, a balanced disk abutment suspended between the adjacent ends of said bore, the periphery of said abutment adapted to revolve transversely across the periphery of the piston disk arm, which carries the piston in said bore, in combination with suspended devices connected with said abutment for automatically varying the position of the abutment, whereby the contact between the two disks is rendered flexible, and grinding or leakage is obviated, substantially as shown and described, and for the purposes herein set forth.

49. In a rotary engine, a balanced disk abutment, rotatable therein, and yieldable means for varying the position of said abutment automatically, substantially as shown and described, and for the purposes herein setforth.

abutment cooperating with the piston member under the influence of gravity, and external means by which the Weight of the abutment is regulated at will, substantially as shown and described, and for the purposes herein set forth.

51. In a rotary engine having an annular cylinder with a bore that is circular in cross section, a self expanding piston rotatable therein, said piston formed with two split rings, one within the other, and movably secured between radially extending ears formed on the periphery of the piston arm, said ears forming the heads of the piston which is connected by a balancing lever with a sliding weight carried on one of said ears, whereby the centrifugal force exerted upon said piston member, when in operation, is automatically neutralized by an equal force exerted in an opposite direction upon the said sliding weight, substantially as shown and described and for the purposes herein set forth.

52. In a rotary engine, having an annular cylinder with a bore that is circular 1n cross section, and provided with one disk for carrying a piston on its periphery, revoluble in said bore, and provided with another disk which serves as an abutment or revolving cylinder-head, the former rigidly secured in position on the main shaft and supported by vertically adjustable main bearings, the latter disk suspended above the former in such a manner as to adapt it to revolve transversely across the former whereby a flexible contact between the peripheries of said disks is established and ample compensation afforded for an increase of their diameters due to the expansion of the metal composing said disks by reason of any increased heat to which they are subjected in the operation of said engine, substantially as shown and described, and for the purposes herein set forth. v

53. In a rotary engine, cylinder provided with a bore that is circular in cross-section, a piston carried by a dlsk secured to the main shaft, and having expanding split packing rings revoluble in said bore, a revolving disk abutment with one or more cut-away sections in its periphery and adapted to freely revolve between the adjacent ends of said bore, of an elongated packing plate located in a cavity surrounding one or both of said adjacent ends of the bore, and adapted to be held in flexible contact against the finished outer surface of said disk abutment by springs, said packing plate being formed of such segmental shape as to equalize the Wear between 1t and the revolving disk, whereby the surhaving an annular

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