GB2089893A - Bi-chamber rotary elastic-fluid engine - Google Patents

Abstract

A valveless turbine-like rotary engine employs two sets of rotor or sealing blades 35, 36, 37; 38, 39, 40, rotating around separate eccentric points on a stationary mutual crankshaft 42 within a drum-type rotor 9 concentrically mounted within an oblong engine chamber 1, 2. The drum-type rotor 9 forms the oblong chamber into two diametrically opposed radial chambers through each of which one set of the rotor or sealing blades pass as the drum 9 rotates. The two sets of blades move radially through equidistant slots arranged within the drum-type rotor 9 so as to be extended into one of the radial chambers, thus varying the effective volume of the respective radial chambers through which they move. Accordingly. the introduction of a pressurized medium through diametrically arranged inlet ports 5, 6 into the radial chambers rotates the blades and the drum. <IMAGE>

Description

SPECIFICATION Valveless bi-chamber rotary steam engine with turbine effect Background of the Present Invention Large rotary machine, specifically a large rotary steam engine, that can be effectively and efficiently run by a variety of power sources have been sought for many years. However, not enough attention was given to the compensation of internal pressures to allow the creation of such an engine that can use relatively low pressures.

Also, since James Watt, large steam engines have required the addition of lubricants to the steam in the form of oil in order to lubricate the large number of sliding parts such as pistons and the various sliding seals. To do otherwise would result in large amounts of friction and wear which, of course, was not desirable.

The known prior art turbine machines have several characteristic disadvantages. For example, conventional turbine machines maintain maximum efficiency only under full load conditions. Thus, under partial load conditions, efficiencies tend to fall rapidly toward zero. Furthermore, constantly high revolution rates are necessary to optimize output from the device, so that reductions in the revolution rate rapidly reduces efficiency.

Moreover, turbine machines are high temperature machines because they utilize the kinetic energy of fast moving gas molecules only and, therefore, need to operate at temperatures above 300 degrees C to achieve respectable efficiencies. The rate of revolution of a conventional steam engine is also limited by the main slide valve which itself generates friction and tends to seize.

It is, therefore, one aim of the instant invention to produce a large, low temperature rotary steam engine in which internal pressures are compensated for and in which sliding friction and wear are reduced which allows very efficient utilization of the expanding pressure force of a non-lubricated, pressurized medium as well as the kinetic energy of fast moving gas molecules within that medium as found in turbine application, thereby maintaining efficiencies under varying load conditions. It also allows operation of a machine without the use of any valves and their resulting limitations.

Summary of the Present Invention The above and other objects of the instant invention are attained by constructing a valveless bi-chamber rotary steam engine, that can exhibit a turbine-like effect, but which functions mainly as an expansion steam engine which utilizes this turbine effect to contribute to the overall efficiency of the device. Thus, this engine can be referred to as a displacement type steam turbine engine.

The term turbine or turbine-like effect refers to the utilization of the kinetic energy of fast travelling gas molecules that impinge upon rotor blades as in conventional turbine.

The present invention includes an outer housing having an elongated inner chamber in which a drum is concentrically and rotatably mounted. The drum includes two outer ends or hubs and a plurality of circumferentially spaced slots which extend along the length of the drum through which two separate sets of a plurality of rotor blades reciprocate. Two diametrically opposed variable volume radial chambers are defined between the drum and the elongated portion of the interior chamber and by mounting the two sets of rotor blades to a stationary, centrally mounted crankshaft, each set of rotor blades rotates through one of the variable volume radial chambers. A pressurized fluid is forced into each chamber at one side and is allowed to exit at the opposite side so as to impinge on and move each rotor blade as it enters and passes through its respective chamber thereby rotating the drum.

By connecting at least one end of the drum to an output shaft, torque is able to be transmitted.

Contactless roller seals are used to seal the reciprocating rotor blades as they move within the slots with sealing between the seals and the drum being of the labyrinth type. Likewise, contactless or frictionless labyrinth sealing is effected between the drum and the interior housing surfaces at the narrowest portion of the interior chamber and between the ends of the rotor blades and the interior surface of the elongated inner chamber defining the radial chambers. Teflon (Registered Trade Mark) coating can be used as desired to further reduce friction and enhance sealing.

Since no parts experience a sliding or rubbing action, except the necessary bearings including those on which the drum is supported, and because all dynamic sealing is done by frictionless labyrinth seals, no lubricant needs to be added to the steam or other working non-self lubricating medium.

At the beginning oi rotation, the torque moment delivered by the kinetic energy of the steam is much smaller than the torque moment delivered by the expansive pressure force of the steam. However, as the rotational speed increases the amount of kinetic energy per revolution increases, thus, adding to the overall efficiency of this machine. Also, the sealing quality of the labyrinth seals increases rapidly with the increase in rotational speed.

Each set of rotor blades tightly follows the inside curvature of its respective radial chamber, thereby subdividing the radial chamber into at least two portions. Thus, the inlet and outlet ports for each radial chamber are continually sealed from each other during the entire engine cycle despite being continually open. Therefore, no valves are necessary.

Through the introduction of a pressurized medium, such as steam, through diametrically opposed inlet ports in the various radial chambers, the pressure on the drum-type rotor plate surface comes to bear on two diametrically opposed rotor plate surface parts in the diametrically opposed radial chambers, whereby a total pressure compensation is attained. Large machines that work with a highly pressurized working medium, such as the rotary steam engine, are technically feasible only when the internal pressure is completely compensated as shown by the instant invention.

It is self-evident that the instant invention is ideally suited for low temperature applications varying from about 1200 to about 1 500 C, especially geothermal applications, and due to its higher overall efficiencies it may supplant conventional turbines in power plants. However, any source of low pressure and low temperature steam or other medium could be used.

Further exemplary applications include, among others, the direct utilization of pressurized air stored in underground cavities and the direct usage of pressurized underground gas, as well as the use of highly corrosive mediums due to the fact that high temperature resistant non-corrosive plastics can be used to construct this engine.

Other objects, features, and characteristics of the present invention, as well as the methods and operation and functions of the related elements of the structure, and to the combination of parts and economies of manufacture, will become more apparent upon consideration of the following detailed description and the appended claims with reference to the accompanying drawings, all of which form a part of this specification, wherein like reference numerals designate corresponding parts in the various figures.

Brief Description of the Drawings The preferred exemplary embodiment can be understood with reference to the drawings in which: FIGURE 1 shows a diagrammatic crosssectional side view of the instant invention; and FIGURE 2 shows a diagrammatic, top, crosssectional view of the instant invention.

Detailed Description of the Preferred Exemplary Embodiment of the Present Invention Turning now to the Figures, the instant invention, as illustrated, is comprised of an engine housing having an upper half engine housing 1 and a lower half engine housing 2, whereby both halves are tightly screwed together through flange rims 3 and 4, thereby defining an elongated, elliptical hollow interior chamber. The upper and lower engine housings 1 and 2, respectively, each contain a steam inlet port 5 and 6, respectively, and steam outlet ports 7 and 8, respectively. Inlet ports 5 and 6 and outlet ports 7 and 8 are diametrically opposed to one another and each pair is located on one side of the engine, as shown in Figure 1, and will service one side or portion of the engine specifically only one radial chamber as will be more fully explained hereafter.

A drum-type rotor 9 is rotatably mounted concentrically within the chamber formed between engine housings 1 and 2, thereby forming that elongated interior chamber into two diametrically opposed radial chambers 10 and 11.

Drum-type rotor 9 is comprised of two outer or end rotor disks 12 and 13. Disk 12 includes a centrally mounted hub 14 which runs on bearing 18. Disk 1 3 includes a centrally mounted shaft 1 5 for power output which runs on a separate bearing 16 and 17. Hub 14 and shaft 15 are, in turn, respectively retained within housing inserts 21 and 22 in which the bearings 18 and 1 6 and 17 are also mounted. To insure proper sealing, packing rings 1 9 and 20 are inserted between disks 12 and 13 and housing inserts 21 and 22, respectively.

The remaining portion of drum 9 is positioned between rotor disks 12 and 1 3 and is comprised of a plurality of drum plates 23, 24, 25, 26, 27 and 28 rigidly mounted to and circumferentially spaced about disks 12 and 13 so as to define a plurality of slots between each plate. Drum plates 23, 24, 25, 26, 27 and 28 each terminate along side edges which define the boundaries of the slots with those side edges being shaped to form a semicircular inwardly bent sealing plate 29 so that two of such plates lie on opposite sides of each slot.

Rotatably mounted inside rotor disks 12 and 1 3 and adjacent the slots in drum 9 on sealed noncorrosive bearings 31 are six circular disks 30.

Four rigid bolts 52 extend outwardly from the surface of each circular disk 30 toward the interior of the drum and rolls 32 are rotatably mounted thereon through sealed non-corrosive needle roller bearings (not shown). Two sealing bars 33 and 34 are mounted on the sides of each circular disk 30 and screwed rigidly together, thus, forming a single sealing unit with rolls 32.

The outside surface of each sealing bar 33 and 34 is formed to follow tightly, but without contact, the concave curvature of sealing plates 29.

The inside surface of each sealing bar 33 and 34 is formed to fit about half the circumference of two rolls 32 without contact. Also, a plurality of thin slots (not shown) are formed so as to extend lengthwise along the outside and the inside surface of each sealing bar 33 and 34 such that a frictionless labyrinth sealing effect is obtained thereby between sealing bars 33 and 34 and sealing plate 29 as well as between sealing bars 33 and 34 and rolls 32.

Further, the outer surfaces of drum plates 23, 24, 25, 26, 27 and 28 are appropriately spaced from the interior surfaces of the interior chamber so that at their closest passage thereto lengthwise slots formed in their exterior surfaces or otherwise therebetween (not shown) create a frictionless labyrinth sealing effect at such points.

The outer narrow surface 80 of rotor blades 35, 36, 37, 38, 39 and 40 also define between themselves and the chambers' interior surface a plurality of lengthwise extending slots (not shown) whereby frictionless labyrinth sealing is also achieved between the ends of each rotor blade and the interior surface of the housing defining the radial chamber. Thus, rotor blades 35, 36, 37, 38, 39 and 40 will be permitted to travel close to, but not in contact with the walls of radial chambers 10 and 11 while simultaneously maintaining a seal with respect to the interior surface of the housing.

Sliding friction is prevented by having rotor blades 35, 36, 37, 38, 39 and 40 contact rolls 32, whereby rolls 32 rotate as rotor blades 35, 36, 37, 38, 39 and 40 reciprocate in and out of the slots in drum 9 move. To enhance the sealing effected at this area, the sides of rotor blades 35, 36, 37, 38, 39 and 40 are preferably teflon coated.

Likewise, rotor blades 35, 36, 37, 38, 39 and 40 will move from one side of the slot to the other as drum 9 rotates and sealing bars 33 and 34 together with sealing plate 29 allow such movement and provide the necessary sealing.

A stationary crankshaft, generally indicated at 82, is comprised of two concentrically situated ends 41 and 44, with one end 41 rigidly secured with wedge pieces 45 into housing insert 21, as shown in Figure 2. The crankshaft is then formed with at least two eccentrically situated crankshaft pieces 42 and 43, on which the sets of rotor blades are attached. Blades 35, 36 and 37 are rotatably mounted to crankshaft piece 43 through suitable connecting rods 46 and respectively sealed non-corrosive bearings 48.

The other set of rotor blades 38, 39 and 40 is rotatably mounted to the other eccentrically situated crankshaft pieces 42 through suitable connecting rods 47 and another set of sealed noncorrosive bearings 48.

The other end 44 of crankshaft 82 is, in turn, mounted within rotor disk 13 through sealed noncorrosive bearing 53 so that disk 1 3 can rotate therearound so that the rigid condition of crankshaft 82 remains, notwithstanding the rotation of drum 9 thereabout. To ease assembly, openings 49 are made in disks 12 and 13 as is best shown in Figure 1.

Outlet ports 7 and 8 are connected to chambers 10 and 11 via small holes 50 leading out of respective engine housings 1 and 2, to aid in reducing sound generation.

Inlet ports 6 and 7, on the other hand, lead to chambers 10 and 11 through maximum sized holes 51 where the medium will engage rotor blades moving there past.

While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention can be employed in various forms and is not to be limited to the disclosed exemplary embodiment but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures.

Claims (14)

1. A displacement type rotary steam turbine engine comprising: a housing having means defining a hollow, elliptical interior chamber.

drum means rotatably and concentrically mounted within said hollow elliptical chamber for forming said hollow chamber into at least two diametrically opposed radial chambers, at least two sets of a plurality of sealing blades, each blade being eccentrically and slidably mounted interiorly of said drum means, each of said sets of blades rotating together with said drum means with each blade being radially movable therein so as to be positioned to effect frictionless sealing between the blades and the walls defining said radial chambers as each blade passes through one of said radial chambers as said drum means rotates, said housing further including inlet and outlet means for allowing entry and exit of a working medium to each of said radial chambers, and power take-off means operatively associated with said drum means for connecting said engine to a utility device, so that as the working medium enters the inlet means for each chamber, the drum means will be rotated by the effect the working medium has on said sealing blades as said sealing blades pass through their respective radial chambers.

2. An engine as in claim 1, wherein said inlet ports direct the pressurized working medium into said radial chambers at an angle with respect to said sealing blades, thereby increasing engine efficiency.

3. An engine as in claim 1 , wherein said drum means includes means for sealing each of said blades as it moves radially with respect to said drum means.

4. An engine as in claim 3, wherein said sealing means comprises a plurality of rollers.

5. An engine as in claim 4, wherein said sealing rollers are teflon coated.

6. An engine as in claim 1, wherein said sealing blades have teflon coated sides.

7. An engine as in claim 1, wherein said housing, said drum means and said sets of sealing blades are made from high temperature resistant, non-corrosive plastic.

8. An engine as in claim 1, wherein each of said sets of sealing blades are mounted to a fixed camshaft centrally positioned within said interior chamber.

9. An engine as in claim 8, wherein said drum means includes two opposing end members each of which is rotatably mounted about said fixed camshaft.

10. An engine as in claim 8, wherein said drum means is comprised of a plurality of separate sections secured so as to define a plurality of axially extending slots through which said sealing blades reciprocate and sealing means movably mounted within said slots for sealing each of said sealing blades within said slots as they move therethrough.

11. An engine as in claim 10, wherein said sealing means provide a rolling seal.

12. An engine as in claim 10, wherein said sealing means includes a pair of mounting members rotatably secured within said two opposing end members so as to be diametrically opposed to one another, first and second sealing bars mounted between said pair of mounting members so as to lie on opposite sides of and spaced from said sealing blades and at least one sealing roller rotatably mounted within each of said first and second sealing bars so as to engage said sealing blade.

13. An engine as in claim 12, wherein means defining labyrinth seals are provided between said rollers and said sealing bars and between said sealing bars and said slots.

14. An engine as in claim 1, wherein said inlet and outlet means include means defining an opening into said housing and a valveless passage extending from said opening directly to said radial chamber.

1 5. An engine substantially as hereinbefore described with reference to and as shown in the accompanying drawings.