US3726188A

US3726188A - Fluid-operated engine

Info

Publication number: US3726188A
Application number: US00124734A
Authority: US
Inventors: R Siebelt
Original assignee: Individual
Current assignee: Fairchild Industries Inc; Shared Technologies Fairchild Telecom Inc
Priority date: 1971-03-16
Filing date: 1971-03-16
Publication date: 1973-04-10
Anticipated expiration: 1990-04-10

Abstract

The engine comprising this invention comprises a rotatable power takeoff drum which encloses a cylindrical cylinder block rotatable with said drum about an axis which is eccentric to that of said drum. A shaft for said block extends through a bore in a main shaft and contains longitudinal fluid inlet and exhaust passages for operating fluid which communicate at the inner ends with the radially innermost ends of cylinder bores which extend radially within said block and said bores have aligned bore sections which have progressively larger diameters outward from the inner ends thereof to provide multi-stage cylinder sections. Connecting rods connect the outer ends of pistons in said bores to the inner surface of the rim of said drum to rotate it as said cylinders communicate successively with said fluid inlet and exhaust passages.

Description

Unite [451 Apr. 10, 1973 Siebelt 1541 FLUID-OPERATED ENGINE [75] Inventor: Raymond J. Siebeit, Largo, Fla.

[73] Assignee: Corinne Siebelt Guntner, Chicago,

[22] Filed: Mar. 16, 1971 [21] Appl. No.: 124,734

[51] Int. Cl. ..F01b 1/06, FOlb 13/06 [58] Field of Search ..91/491, 498, 495, 91/482 [56] References Cited UNITED STATES PATENTS 1,300,706 4 191 9 Duby .j ..91/495 2,054,110 9/1936 Worth 91/495 2,474,536 6/1949 Lundegard... ,....9l/495 2,737,122 3/1956 Tacconi 1 ..91/498 3,058,429 10/1962 Rocheville ..91/495 Primary Examiner-Paul E. Maslousky Attorney-C. Hercus Just The engine comprising this invention comprises a rotatable power takeoff drum which encloses a cylindrical cylinder block rotatable with said drum about an axis which is eccentric to that of said drum. A shaft for said block extends through a bore in a main shaft and contains longitudinal fluid inlet and exhaust passages for operating fluid which communicate at the inner ends with the radially innermost ends of cylinder bores which extend radially within said block and said bores have aligned bore sections which have progressively larger diameters outward from the inner ends thereof to provide multi-stage cylinder sections. Connecting rods connect the outer ends of pistons in said bores to the inner surface of the rim of said drum to rotate it as said cylinders communicate successively ABSTRACT with said fluid inlet and exhaust passages.

7 Claims, 14 Drawing Figures PATENTEDAPRI 01973 SHEET 1 HF Q IN VE N TO K A24 mow J 5/5/3511 FLUID-OPERATED ENGINE BACKGROUND OF THE INVENTION Various types of steam turbines have been developed which contain radially extending vanes through which steam under pressure is forced in order to rotate the rotor of the turbine. Turbines of this type also have long been provided with multi-stages or sections, the smallest of which usually receive the steam pressure initially at the inlet pressure and as the exhausting steam discharges through various sections, the steam at progressively lower pressures is nevertheless utilized in succeeding lower pressure sections of the turbine to continue to provide rotating forces. This results in economical utilization of steam pressure.

Many types of steam engines have been devised which utilize reciprocating pistons which operate a connecting rod that drives the crank connected to a power take-off, most such devices also including a fly wheel. Engines of both of the foregoing types however do not lend themselves to being constructed in compact manner so as to occupy a minimum amount of 3- dimensional space.

At present, there is considerable pressure on automobile manufacturers to minimize the discharge into the atmosphere of polluting contaminants from the exhausts of gasoline powered engines. This has resulted in some manufacturers giving attention to designing useful types of steam engines which, while requiring fossil type fuel of some kind to heat water or other vaporiza ble liquid to provide gaseous fluid volumes under pressure to operate the engine, nevertheless discharge a minimum amount of polluting gaseous or solid materials into the atmosphere. In view of this, the present invention is directed to the design of a fluid-operated engine which, specifically, preferably is operated by steam pressure but nevertheless also can be operated by other forms of gaseous fluids under pressure, including compressed air.

SUMMARY OF THE INVENTION It is the principle object of the present invention to provide a fluid-operated engine which includes a main shaft which is supported stationarily at one end and the opposite end rotatably supports a cylindrical drum which is a power takeoff member that may comprise a pulley, ring gear or the like, said drum completely enclosing a cylindrical cylinder block which is supported by an auxiliary shaft rotatably mounted in a bore in the main shaft which is eccentric to the axis of the main shaft, the cylinder drum being rotatable about said auxiliary shaft. Radially extending multi-stage cylinder bores are formed in evenly circumferentially spaced locations within the cylinder block and pistons, that are complementary in shape to the cylinder bores, are reciprocable therein and the outer ends of the pistons are connected by connecting rods to the inner surface of the cylindrical drum, whereby the reciprocation of the cylinders within the cylinder bores by means of fluid pressure results in the cylindrical drum being rotated about its axis while the cylinder block is simultaneously rotated about said auxiliary axis. Fluid passages extend between the sections of each of said multi-stage bores of said composite cylinder bores, whereby fluid which is initially introduced to the section of smallest diameter acts against the corresponding piston section therein and a certain amount of the fluid pressure bypasses said section and moves to the next adjacent section to discharge against the piston section therein and enhance the outer movement of the piston, while a portion of the operating fluid from said last mentioned section by-passes the same and is moved to the outermost piston section for operation thereagainst and thereby effects the final discharge of fluid pressure against such outermost section of the piston.

Another object of the invention is to provide means by which the auxiliary shaft may be rotated a limited amount, such as not more than in one direction or the other, about its axis for purposes of changing the direction of rotation of the power takeoff drum.

A further drum object of the invention is to provide flexible connections for the outer ends of the fluid inlet and exhaust passages in the auxiliary shaft and the sources of fluid pressure and fluid discharge means in order to permit operation of the rotation of the auxiliary shaft to effect such change in direction of rotation of the power takeoff drum.

Still another object of the invention is to provide a plurality of radially extending passages between each multi-stage cylinder bore thereof and a plurality of such passages preferably are provided at circumferential locations which are spaced apart by even distances.

Details of the foregoing objects and of the invention, as well as other objects thereof, are set forth in the following speciflcation and illustrated in the accompanying drawings comprising a part thereof.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an end view of an exemplary fluid-operated engine embodying the principles of the present invention.

FIG. 2 is a side elevation of the engine shown in FIG. 1.

FIG. 3 is a vertical sectional view of the engine shown in FIG. I as seen on the line 33 thereof.

FIG. 4 is a vertical sectional elevation of the interior of the engine shown in FIG. 3, as seen on the line 44 thereof.

FIG. 5 is a vertical transverse section of the righthand end portion of the engine shown in FIG. 3, said view being taken substantially midway between the -opposite parallel end faces thereof.

FIG. 6 is a fragmentary longitudinal section of the auxiliary shaft of the engine shown on larger scale than in the preceding figures, as viewed on the line 6-6 of FIG. 7.

FIG. 7 is a transverse sectional view of the auxiliary shaft shown in FIG. 6 as seen on the line 7-7 thereof.

FIG. 8'is an end view of the upper end of one of the pistons otherwise illustrated in FIGS. 3 and 5.

FIG. 9 is a side elevation of the pistons shown in FIG. 8 and also illustrating fragmentarily, in phantom, one end ofa connecting rod for said piston.

FIG. 10 is a fragmentary view showing the outer end of one of the cylinder bores formed in the cylinder block shown in FIGS. 3 and 5.

FIG. 11 is a fragmentary vertical sectional view of the cylinder bore shown in FIG. 10 as seen on the line 1lll ofsaid figure.

FIG. 12 is a side elevation of an exemplary connecting rod for said piston such as shown in FIGS. 8 and 9.

FIGS. 13 and 14 respectively are front and side elevations of connecting links which extend between the cylinder block and cylindrical power takeoff drum of the engine, FIG. 14 being a view as seen on the line 1414 of FIG. 13.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The exemplary illustration of fluid-operated engine shown in the drawings hereof is intended to be mounted upon a suitable supporting base of any appropriate kind. It may be a vehicle which is to be driven by the engine 12, or any other device with which the engine is to operated. A supporting member 14 of appropriate type and size is connected by bolts 16, or otherwise, to the base 10. The upper end of supporting member 14 is provided with a circular seat member 18 which is bi-partite and somewhat resembles a journal bearing. Said member includes a cap 20 which is secured by bolts 22 to the lower half 24 of the member 18-for purposes of receiving, and securely clamping against rotation, one end of a relatively short main shaft 26.

The shaft 26 is provided with an eccentric bore 28 which rotatably receives an auxiliary shaft 30. One end of the auxiliary shaft 30 extends outwardly beyond the adjacent end of main shaft 26. Connected to said projecting end is a clamping means 32 which surrounds the shaft and is provided with a radially extending positioning arm 34 by means of which the rotary position of the auxiliary shaft 30 is determined and maintained with respect to main shaft 26.

A cylindrical cylinder block 36 is provided with a central bore 38 which receives the opposite end of auxiliary shaft 30 which projects beyond the right-hand end of main shaft 26, as viewed in FIG. 3. Suitable bearings 40 which preferably are antifriction type are mounted in suitable seats in opposite faces of the cylinder block 36 for engagement with the auxiliary shaft 30. The cylinder block 36 is provided with a series of compound type, multi-stage cylinder bores 42 which respectively slidably receive pistons 44 that are complementary in shape to the bores 42. Details of the cylinder bores and pistons are set forth hereinafter.

The cylinder block 36 is enclosed within a cylindrical power takeoff drum 46. The periphery of said drum may comprise suitable power takeoff means such as by serving as a large pulley or sprocket gear around which an endless flexible member 48 may extend for transmission to device to be driven thereby. Otherwise, if desired, the drum 46 may have gear teeth formed thereon entirely around the periphery thereof for engagement with teeth of other gears to be driven thereby. Therefore, the flexible endless member 48 which is illustrated in FIG. 1 is solely exemplary and not restrictive.

Extending from one face of drum 46 is a bearing boss 50 which contains a pair of anti-friction bearings 52 that surround the main shaft 26 for support of the drum 46 thereby. The opposite face 54 of the drum preferably is removable therefrom to proVide means of access to the interior of the drum 46. Any suitable means may be employed to secure the removable cover member 54 relative to the face of the drum 46 within which it is received, preferably in a fluid-tight manner.

For purposes of delivering fluid pressure, such as steam, compressed air, or otherwise, to the inner ends of the compound type cylinder bores 42 of cylinder block 36 and discharging the same therefrom, the auxiliary shaft 30 is provided with a pair of longitudinally extending

bores

56 and 58 which respectively are connectable at the outer ends thereof to a source of fluid,

under pressure, and fluid discharge means, not shown.

The transmission of such fluids is made possible preferably by flexible conduits 60 and 62 which are shown in phantom in FIG. 1.

Referring to FIGS. 5-7, and especially FlGS.-6 and 7, it will be seen that the inner ends of the pressure fluid conduit 56 communicates with an arcuate peripheral recess 64 and the inner end of the exhaust fluid bore 58 communicates with a similar arcuate peripheral recess 66. The function of these arcuate recesses is best understood from FIG. 5 wherein it will be seen that the inner ends of all of the compound multi-stage cylindrical bores 42 extend into and communicate with the central bore 38 of the bearing block 36 and thereby successively communicate respectively with the

arcuate recesses

64 and 66 as the bearing block 36 and drum 46 rotate about their respective axes which, due to the eccentric mounting of the auxiliary shaft 30 with respect to main shaft 26, renders said respective axes similarly eccentric to each other. As seen from FIGS. 6 and 7, short communicating holes 68 extend between the

bores

56 and 58 and the corresponding

arcuate recesses

64 and 66 for transmission of fluid therebetween.

To operably connect the cylinder block 36 with the power takeoff drum 46 in order that the latter may be rotatably driven by the former, the outer end 70 of each piston 44 is provided with a suitable socket 72 which is intersected by a transverse hole 74 through which a wrist pin 76 extends so as to pivotally connect one end of a connecting rod 78 thereto. The opposite end of each connecting rod is connected by a pivot pin 80to the inner surface of drum 46 which is provided with appropriate arcuate recesses to receive said opposite ends of each connecting rod 78. Pivot pins 80 extend inward from one outer face of the drum 46 and may be suitably connected by appropriate threads, not

shown, so as to be locked in operative position until it is necessary to remove the same for repair or replacement.

Referring particularly to FIGS. 3, 5, 10 and 11, it will I be seen that each cylinder bore 42 actually consists of three cylindrical bore sections. The largest section 82 is outermost. Next is an intermediate cylindrical bore section 84, and innermost is a smaller cylindrical bore section 86 which at its inner end communicates with the central bore 38 of the cylinder block 36. The multi-sec- In order to provide means for the transmission of operating fluid, under pressure, to the various bore sections of each cylinder bore, said bores are provided with a plurality of radial slots 94 which, particularly in FIGS. 3, 5 and 11, appear to be pairs of acute triangles. Nevertheless, such passage means are effective to provide adequate transmission of both pressure fluid as well as exhaust fluid between the respective operating faces of the piston sections and the fluid inlet and discharge arcuate transmission recesses 64 and 66, as well as the transmission bores 56 and 58 in the auxiliary shaft 30.

Due to the eccentric position of the cylinder block 36 with respect to the interior of the power transmission drum 46 within which it is contained, notwithstanding the fact that there is uni-directional rotatary bearing bores formed in the inner surfaces of the radially extending face of drum 46, which is integral,

with bearing boss 50, and the adjacent face of cylinder block 36, as can be best seen from FIGS. 3. The length of said links and the disposition of the pintles 98 therein has been calculated to be such that the necessary amount of migratory movement in limited opposite rotary directions may occur between cylinder block 36 and drum 46 to permit the axial movements of the pistons 44 within the bearing bores 42 therefor and thereby enable the connecting rods 78 to propel the drum 46 rotatably about its axis which is coincident with that of the main shaft 26, while the bearing block 42 rotates about the auxiliary shaft 30.

Particularly by reference to FIGS. 1, 5 and 7, it will be seen that if the positioning arm 34 is manipulated to rotate it through an are no greater than 180 in order to rotatably shift the auxiliary shaft 30 about its axis, the positions of the arcuate

peripheral recesses

64 and 66 will substantially be reversed with respect to the innermost ends of the cylindrical bores 42 and thereby will change the direction of rotation of the drum 46 and cylinder block 36. Further, from FIG. 7 in particular, it will be noted that the arcuate extent of the pressure recess 64 is less than that of the exhaust recess 66. This arrangement is preferred in order that no undue impedence will be produced relative to exhausting the pressure fluid from the cylinder bores in which the pistons are moving inwardly while the inner end of a smaller number of the pistons are receiving pressure fluid in order to move the pistons radially outward within the cylinder bores therefor.

By referring to FIG. 5 especially, it will be seen that in the exemplary arrangement of pistons'and complementary bores therefor, a total of eight has been illustrated. Of this quantity, it will be seen from the lefthand portion of said figure that the inner ends of three of the cylindrical bores are in communication with the peripheral recess 64 from which fluid pressure is being delivered to such bores. At such time, a total of at least four of the inner ends of the cylinder bores 22 are in communication with the peripheral recess 66 through which exhaust fluid is being conducted to the exhaust conduit 58 for discharge through the flexible conduit 62. Also, with reference to FIG. 1, it will be seen that the flexible nature of the inlet and exhaust flexible conduits 62 readily permits the reversal of position of the auxiliary shaft 30 by means of the manipulating member 34 in the manner described above.

From the foregoing, it therefore will be seen that the with the axis of the main shaft 26 about which the drum 46 rotates. Suitable clutch means, or otherwise, not shown, can be employed in conjunction with such an arrangement.

Further, the provision of a multi-stage cylinder and piston arrangement in the engine insures maximum efficiency in the consumption of fluid pressure power furnished to the engine. In addition, to enhance the efficiency of power furnished to the engine, sealing means such as piston rings may be utilized but such rings need only be provided on the largest piston section 88, for example, of each piston. Such piston rings are not illustrated in detail but it will be understood that one or more of the same may be provided, of a conventional nature, within appropriate annular grooves formed in the peripheries of said largest sections 88 of the pistons.

While the invention has been described and illustrated in its several preferred embodiments, it should be understood that the invention is not to be limited to the precise details herein illustrated and described since the same may be carried out in other ways falling within the scope of the invention as illustrated and described.

I claim:

1. A fluid-operated engine comprising in combination, a supporting member, a main shaft non-rotatably supported at one end by said member and having a bearing bore extending longitudinally therethrough eccentrically to the axis thereof, an auxiliary shaft rotatably mounted within said bearing boreand one end thereof extending beyond the opposite end of said main shaft, a cylindrical cylinder block supported rotatably upon said one end of said auxiliary shaft, a cylindrical power takeoff drum completely enclosing said cylinder block, bearing means supporting said drum rotatably and coaxially upon said main shaft, fluid inlet and exhaust passages extending axially through said auxiliary shaft and terminating at the inner end in arcuate peripheral recesses disposed in the portion of said shaft which supports said cylinder block, said cylinder block having a plurality of similar circumferentially spaced and radially extending cylinder bores therein each having a similar series of progressively smaller diameter cylindrical sections extending from the outer ends to the inner ends thereof and the inner ends communicating successively with said peripheral recesses in said auxiliary shaft as said cylinder block rotates thereon, fluid passages extending transversely outward from the walls of said sections of said bores and also extending between said sections of each cylinder bore for passage of pressure and exhaust fluid therebetween, similar pistons complementary in shape to said cylinder bores reciprocable axially therein, connecting rods extending between and connected at opposite ends respectively to the outer ends of said pistons and pivot means circumferentially spaced evenly around the inner periphery of said drum to effect rotation of said drum around said main shaft as said pistons successively move outwardly in said cylinder bores, and link means extending between said cylinder block and drum to maintain the same in coordinated rotary relationship.

2. The engine according to claim 1 further characterized by fluid passages which extend between said sections of said cylinder bores comprising radial slot means formed in the walls of said sections.

3. The engine according to claim 2 in which a plurality of said radial slot means are formed in the walls of said cylinder bores at circumferentially'spaced locations.

4. The engine according to claim 2 in which said slot means extend substantially from the inner end of the cylinder bore section of smallest diameter to the inner end of the cylinder bore section of largest diameter.

' 5. The engine according to claim 1 in which the section of each piston of largest diameter has at least one piston ring therein to minimize escape of fluid under pressure between the cylinder bore walls and piston walls.

6. The engine'according to claim 1 further including means connected to said auxiliary shaft and operable to rotate the same about its axis to shift the positions of said arcuate peripheral recesses relative to said cylinder block to change the direction of rotation of said power takeoff drum.

7. The engine according to claim 6 further including flexible means connected to said fluid inlet and exhaust passages and also being connectable respectively to a source of fluid pressure and fluid discharge means.

Claims

1. A fluid-operated engine comprising in combination, a supporting member, a main shaft non-rotatably supported at one end by said member and having a bearing bore extending longitudinally therethrough eccentrically to the axis thereof, an auxiliary shaft rotatably mounted within said bearing bore and one end thereof extending beyond the opposite end of said main shaft, a cylindrical cylinder block supported rotatably upon said one end of said auxiliary shaft, a cylindrical power takeoff drum completely enclosing said cylinder block, bearing means supporting said drum rotatably and coaxially upon said main shaft, fluid inlet and exhaust passages extending axially through said auxiliary shaft and terminating at the inner end in arcuate peripheral recesses disposed in the portion of said shaft which supports said cylinder block, said cylinder block having a plurality of similar circumferentially spaced and radially extending cylinder bores therein each having a similar series of progressively smaller diameter cylindrical sections extending from the outer ends to the inner ends thereof and the inner ends communicating successively with said peripheral recesses in said auxiliary shaft as said cylinder block rotates thereon, fluid passages extending transversely outward from the walls of said sections of said bores and also extending between said sections of each cylinder bore for passage of pressure and exhaust fluid therebetween, similar pistons complementary in shape to said cylinder bores reciprocable axially therein, connecting rods extending between and connected at opposite ends respectively to the outer ends of said pistons and pivot means circumferentially spaced evenly around the inner periphery of said drum to effect rotation of said drum around said main shaft as said pistons successively move outwardly in said cylinder bores, and link means extending between said cylinder block and drum to maintain the same in coordinated rotary relationship.

3. The engine according to claim 2 in which a plurality of said radial slot means are formed in the walls of said cylinder bores at circumferentially spaced locations.

5. The engine according to claim 1 in which the section of each piston of largest diameter has at least one piston ring therein to minimize escape of fluid under pressure between the cylinder bore walls and piston walls.

6. The engine according to claim 1 further including means connected to said auxiliary shaft and operable to rotate the same about its axis to shift the positions of said arcuate peripheral recesses relative to said cylinder block to change the direction of rotation of said power takeoff drum.