US752604A - Rotary engine - Google Patents

Description

No. 752,604. PATENTED FEB. 16, 190.4. E. F. TAYLOR. ROTARY ENGINE.

APPLICATION P'ILBD JAN. 13, 1904. no MODEL. 3 SHEETS-SHEET 1.

Snuenfoz jz zylor 93,: M W

No. 752,604. v v P'ATENTBD FEB. 16, 1904. E. F. TAYLOR.

ROTARY, ENGINE.

APPLICATION I'ILED.JAN.13. 1904. 7 NO MODEL. 3 SHEETS-SHEET 2 wumvboz No. 752,604 PATENTE11PEB.l6,1904.

E. r. TAYLOR. ROTARY ENGINE.

APPLICATION FILED JAN. 13, 1904.

N0 MODEL. 3 SHEETS-SHEET 3.

Tar-.2; 3 Flair.

I u Edwin E 755 1? ma norms warms co. yummy-won wAsmNe'rwL-u. c.

Patented February 16,1904.

PATENT OFFICE.

EDWIN F. TAYLOR, OF NEW DECATUR, ALABAMA.

ROTARY ENGINE;

SPECIFICATION forming part of Letters Patent No. 752,604., dated February 16, 1904.

Application filed January 13,1904. Serial No. 188,869. (No model.)

To alZ whom it may concern.-

Be it known that I, EDWIN F. TAYLOR, a citizen of the United States, residing at New Decatur, in the county of Morgan and State of Alabama, have invented certain new and useful Improvements in Rotary Engines; and I do hereby declare the following to be a full, clear, and exact description of the invention, such as will enable others skilled in the art to which it appertains to make and use the same.

In an application for patent filed by me August 22, 1902, Serial No. 120,718, I have shown, described, and claimed a rotary engine having a wheel driven by the kinetic impact and reactive forces of a motive fluid which is adiabatically partially expanded in advance of the application of each of said forces, whereby the velocity of the wheel is brought within rotary engine equipped with a reversing mechsafety limits.

In a divisional application for patent filed by me October 9, 1903, Serial No. 176,368, I have shown, described, and claimed a rotary engine embodying the above-stated adiabatic principle and consisting of a series of wheels against each of which is directed an equal amount of energy of the motive fluid.

My present invention relates to a reversing mechanism which whilecapable of utilization in connection with rotary engines generally is designed more especially for use with my improved type of engine containing the series of wheels. The improved reversing mechanism'is therefore shown as applied to the engine forming the subject-matter of mydivisional application above referred to, although such showing is not to be regarded as a' limitation; and it is further understood that the reversing mechanism hereinafter set forth may be variously modified without exceeding the scope of the concluding claims.

In the drawings, Figure 1 is a vertical sec tional view of a portion of a multiple-wheel anism embodying my invention. Fig. 2 is a cross-sectional view on line 2 2 of Fig. 1. Figs. 3 and tare respectively side and front views of one of the nozzle-carrying disks. Fig. 5 is a detail plan view of a portion of a wheel and adjacent chamber, showing the parts for effecting rotation in one direction.

to fasten the parts together.

Fig. 6 is a similar view showing parts of the same wheel for effecting reverse rotation. Figs. 7 and 8 are views of divided chambers between the wheels. Fig. 9 is an enlarged sectional view on line 9 9 of Fig. 1. Fig. 101$ a detail view, partly broken away, of the gova forwardly-extending flange 7 bolted to the casing-head 8 and having a reduced outer portion 9 confined between said casing and head, bolts 10, passed through flanges of the casing and head and through said portion 9, serving In the ring are circular openings 11, in each of which is rotatably confined a disk 12, having its inner face flush with the rearface of the ring and having aflange 13 entering an enlargement of said opening. Each wheel 2 is provided in its rim portion 14 with two concentric sets of vanes or buckets 15 16, separated by an imperforate ring portion 17, between which and the ring no clearance is provided, whereby the two sets of vanes or buckets have no intercommunication. The vanes mayall have the concavo-convex form shown; but the outer set of vanes 16 have their concave surfaces facing a direction opposite tothat of the concave impact surfaces of the inner set of vanes 15. (See more particularly Figs. 5 and 6.) The imperforate ring portion of the first wheel of the series travels centrally across the disks 12 without clearance, and each of said disks is provided at one side of its center with a section 18 of an adiabatic line or curvefluid-port, which portfhereinafter termed nozzle-section) may have its diverging walls formed by the material of the disk or may be asepa rate tube inserted in' an opening provided therefor in the disk, as desired. The nozzlesection, in which the fluid is adiabatically exthe chamber being formed by a ring 6, having panded, extends through the disk at an angle to the axis of the latter and discharges the motive fluid delivered thereto from the chamber 4 against the inner set of vanes to revolve the wheel in one direction, the discharge end of said nozzle-section being in the path of movement of said vanes. The inner and outer sets of vanes are disposed equidistantly from a line central of the series of disks, and by giving the disks a one-half revolution the nozzle-sections are brought into the path of the outer set of vanes with their inclination reversed to revolve the wheel in the opposite direction. By this simple act of turning the disks in their bearings the discharge ends of the nozzle-sections are brought into the path of either of the two sets of vanes, dependent upon the desired direction of revolution of the shaft, and in turning a reversal of the inclination of the nozzle-sections is accomplished, whereby equal 'efliciency is obtained regardless of the direction of running. Obviously any number of disks equipped with nozzle-sections may be provided, dependent upon the power to be exercised on the vanes. The means employed for turning the disks is also simple. One-half of the periphery of the flange 13 of each disk is provided with gear-teeth 19, which mesh with similar teeth 20, formed in the inner side of a gear-ring 21, rotatably confined in the chamber 4 at the re- .duced portion of the ring 6. In the outer side of the gear-ring are teeth 22, meshing with a mutilated pinion 23, suitably journaled on the casing and equipped with a lever 24, by which it is partially rotated to revolve the disks through the medium of the gear-ring. The described parts are constructed to obtain a limited and simultaneous movement of the disks, preferably one-half a revolution, whereby the proper disposition of the nozzle-sections with reference to the sets of vanes is always assured.

Between the rim portions of the wheels 2 2 are annular chambers 25, each receiving partlyexpanded fluid from an adjacent wheel and delivering the same for further expansion into other nozzle-sections at the next wheel, it being understood that the several nozzle-sections at the several wheels constitute practically complete adiabatic line or curve fluid-ports in which complete adiabatic expansion of the fluid is obtained. In one wall of the chamber are channels formed by fixed vanes 26, disposed at an angle to the wheel-vanes, and thus providing reaction-surfaces whereby the adjacent wheel, which travels across said vanes without clearance, is revolved by the combined impact and reactive forces of the fluid. The fluid e11- tering the chamber through said channels discharges therefrom, through diverging nozzlesections 27 in the opposite chamber -wall, against the vanes of the next wheel with an equal amount of energy, and so onthroughout the series of wheels, the exhaust occurring after complete expansion is accomplished. Each chamber is divided by a ring-partition 28 into two inner and outer chambers, each of which has its own inlet-passages formed by the fixed vanes and its own discharging nozzle-sections. The ring-partitions are in alinement with each other and with the imperforate ring portions of the several wheels. Consequently the inner and outer sets of vanes of the wheels are respectively in register with the inner and outer sections of chambers 25. Fluid discharged from the nozzle-sections in the disks against the inner set of vanes to rotate the shaft in one direction is therefore compelled to pass through the several inner chamber-sections and against the several inner sets of vanes, whereas if the disk is turned to effect the reversal of the engine the fluid is compelled to traverse the outer chambers and to impact against the outer sets of vanes. Practically no clearance is provided between the rim portions of the wheels and the chamber-walls and leakage of the fluid from one set of wheel-vanes to the other set is avoided. As a further safeguard against leakage, how ever, I employ fluid-packing annular grooves 29 in the chamber-walls, into which grooves travel annular ring-tongues 30, carried by the wheels. By this provision leakage such as described is absolutely prevented, any fluid or vapor entering between the tongue and groove serving as a packing to prevent the passage of the fluid from the inner to the outer set of vanes, and vice versa.

As a means for governing the supply of fluid to the nozzle-sections in the disks I employ a ring-valve 31, which is mounted in the fluidchamber 4: to be rotated across the series of disks and is provided with an inner series of converging openings 32, 33, 3e, and 35, registering with the inner set of vanes 15 and inner intervening fluid-chambers, and with an outer series of converging openings 36, 37, 38, and 39, registering with the outer vanes and chambers. The openings of each series will conform in number to the number of disks employed, although, for example, I have limited the number of openings in each series to four, which is the number of disks selected for the purpose of illustration. The inner and outer openings are in pairs, respectively located at the disks, and the inner and outer openings of each pair are so disposed (see Fig. 10) as to bring one or the other in register with the receiving end of the nozzle-section in the disk, dependent upon the turned position of said disk. For example, with the disk in the position shown in Fig. l the receiving end of the nozzle-section is in register with the inner opening 32, whereas when the disk is given a one-half revolution the receiving end of the nozzle-section is brought into register with the outer opening 36, and this change in position occurs throughout the entire series of disks. By so disposing the valve-openings the receiving ends of the nozzle-sections are always in register with one set of openings, the other set being out of register until the disks are turned as described. The openings of the several pairs increase in area, being elongated in the direction of movement of the ring-valve, whereby the nozzle-sections in the disks are successively closed and opened to regulate the quantity of fluid to be admitted to the wheels. For example, if the openings 32 36 are each one-eighth of an inch in diameter the next openings, 33 37,will be one-eighth of an inch longer, the third pair three-eighths, and the fourth pair one-half an inch. If, therefore, the valve is rotated to close the first three nozzle-sections, the fourth nozzlesection will still be open, and a further movement of the valve a distance of one-eighth of an inch will be required to completely out off the fluid from the wheels.

Any suitable means may be employed for rotating the ring-valve to close and open the nozzle-sections. A convenient means consists of a short shaft 40, journaled in a packed bearing 41 in the head 8, which shaft has at its inner end a crank 42, connected with the ringvalve by a pin 43. The shaft has at its outer end a crank 44:, to which is pivoted one end of a rod 4C5, the other end having flexible connection with a lever 46, raised and lowered by the action of a ball-governor 47, geared to the shaft 3. To enable the adjustment of the ringvalve by hand to control the supply of fluid, I connect with the rod 45 a hand-lever 48 and equip the same with suitable hand-released locking means, such as shown at 49. Vertical movement of the rod 45 by hand or by the action of the governor effects the partial rotation of the ring-valve through the medium of the crank-shaft, it being understood that the governor is disconnected when hand adjustment is desired. It will be observed that by the use of the hand means for controlling the nozzle-sections the running of the engine can be brought'to the desired speed without throttling the fluid at the throttle-valve. In this way full pressure in the fluid-chamber is always maintained, with the consequent economy and maximum efficiency of the fluid. Moreover, the hand means employed enables a control of the energy at the wheels not attainable by adjustment of the throttle-valve or equivalent means. Condensation of the fluid, with the consequent reduction in weight, is prevented by the use of a fluid chamber or jacket 50, which envelops the engine-casing. To control the expansions of the fluid in its passage through the engine and obtain an equal velocity of the fluid at each of the wheels, I provide in the inner and outer sections of the chambers 25 fluid-pockets formed by partitions 51, Figs. 7 and 8, which pockets correspond in number and positions to the number and positions of the initial nozzle-sections. If the ring-valve is, for example, moved to cover the first three of the nozzle-sections, leaving the fourth uncovered, the partially-expanded fluid discharging from said fourth nozzle-section exerts its energy through change in entropy on the first wheel and enters the pocket in the chamber corresponding in position to the fourth nozzle-section, the first three pockets registering with the first three nozzle-sections being blocked off by the partitions of the pocket in use. These pockets vary in size with each succeeding wheel. Consequently the proper partial expansion is obtained in the several nozzle-sections and an equal amount of energy is exerted on each wheel. The fluid is therefore controlled by the size of the pocket, which size is in proportion to the volume of fluid which has exerted its energy on the previous wheel.

I claim as my invention 1. In a rotary engine, a moving part having oppositely-facing sets of impact-surfaces, and an element having a fluid-port said element being revoluble to present'the port to either of said sets of impact-surfacesl 2. In a rotary engine, a moving part having oppositely-facing sets of impact-surfaces, and a revoluble disk having a fluid-port at an angle to its axis and adapted to present said port to either of said sets of impact-surfaces.

3. In a rotary engine, a moving part having two oppositely-facing concentric sets of impact-surfaces, and a revoluble disk the center of which is midway between the paths of movement of said sets of surfaces, said disk having at one side of its center a fluid-port extending at an angle to its axis, and means for revolving the disk to bring the discharge end of the port in the path of either set of impact.- surfaces.

4. In a rotary engine, a wheel having inner and outer concentric sets of vanes the surfaces of one set facing a direction opposite to that of the other surfaces, an imperforate portion between said sets, a disk the center of which is midway between the paths of movement of said vanes, said disk having at one side of its center an adiabatic line or curve fluid-port section extending through the disk at an angle to the axis of the latter, teeth on the disk and a movable rack meshing with said teeth and adapted to partially revolve the disk to bring the discharge end of the port-section in the path of either set of vanes.

55. In a rotary engine, a series of wheels each having inner and outer concentric sets of vanes, a main fluid-chamber at the first wheel, inner and outer fluid-chambers between the wheels respectively registering with the inner and outer sets of vanes, a disk at the first wheel carrying a fluid-port, and means for rotating the disk to bring the port into the path of either set of vanes.

6. In a rotary engine, a series of wheels each having inner and outer concentric sets of vanes, a main fluid-chamber at the first wheel,

inner and outer fluid-chambers between the wheels respectively registering with the inner and outer sets of vanes, a revoluble disk in the main chamber mounted with its axis between the sets of vanes ofthe first wheel said disk having at one side of its axis a fluid-port extending at an angle to said axis, and means for revolving said disk to bring the discharge end of the port in the path of either set of vanes of the first Wheel. I

7. In a rotary engine, a series of Wheels each having inner and outer concentric sets of van es, inner and outer fluid-chambers between the wheels respectively registering with the inner and outer sets of vanes, a series of revoluble disks at the first Wheel each having at one side of its center a fluid-port adapted to be brought into the path of movement of either set of vanes in the first wheel, means for simultaneously revolving said disks, and partitions in the chambers dividing the same into pockets which are respectively in line with the disks.

8. In a rotary engine, a wheel having inner and outer concentric sets of vanes, a disk having a fluid-port and adapted to be revolved to present the port to either set of varies, and a valve at said disk for regulating said port.

9. In a rotary engine, a wheel having inner and outer concentric sets of vanes, a disk having a fluid-port and adapted to be revolved to present the port to either set of vanes, and a ring-valve having an opening adapted in the rotary movement of the ring valve to be brought into and carried out of register with said port.

10. Inarotary engine, a wheel having inner and outer concentric sets of vanes, a plurality of revoluble disks each having an inclined fluid-port at one side of its axis said port adapted to discharge against either set of vanes, a revoluble ring-valve having inner and outer openings arranged in pairs one pair for each disk, and means for moving said valve.

11. In a rotary engine, a wheel having inner and outer concentric sets of vanes, a plurality of revoluble disks each having an inclined fluid-port at one side of its axis said port adapted to discharge against either set of vanes, a revoluble ring-valve having inner and outer openings arranged in pairs one pair for each disk, the area of said pairs of openings increasing consecutively, a governor connected with said valve, and hand means for operating the valve independently of the governor.

12. In a rotary engine, a series of revoluble W. R. How, W. A. BIBB.

Images