CA1179946A - Valveless bi-chamber rotary steam engine with turbine effect - Google Patents
Valveless bi-chamber rotary steam engine with turbine effectInfo
- Publication number
- CA1179946A CA1179946A CA000391929A CA391929A CA1179946A CA 1179946 A CA1179946 A CA 1179946A CA 000391929 A CA000391929 A CA 000391929A CA 391929 A CA391929 A CA 391929A CA 1179946 A CA1179946 A CA 1179946A
- Authority
- CA
- Canada
- Prior art keywords
- sealing
- engine
- blades
- drum
- rotor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Hydraulic Motors (AREA)
- Sealing Devices (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Abstract
ABSTRACT
A valveless turbine-like bi-chamber rotary steam engine employing two sets of rotor or sealing blades, rotating around separate eccentric points on a stationary mutual crankshaft within a drum-type rotor concentrically mounted within an oblong engine chamber. The drum-type rotor 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 rotates. The two sets of blades move radially through equidistant slots arranged within the drum-type rotor so as to be extended into one of the radial chambers, thus, varying the volume of the respective radial chambers through which they move.
Accordingly, the introduction of a pressurized medium through diametrically arranged inlet ports into the radial chambers rotates the blades and the drum.
A valveless turbine-like bi-chamber rotary steam engine employing two sets of rotor or sealing blades, rotating around separate eccentric points on a stationary mutual crankshaft within a drum-type rotor concentrically mounted within an oblong engine chamber. The drum-type rotor 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 rotates. The two sets of blades move radially through equidistant slots arranged within the drum-type rotor so as to be extended into one of the radial chambers, thus, varying the volume of the respective radial chambers through which they move.
Accordingly, the introduction of a pressurized medium through diametrically arranged inlet ports into the radial chambers rotates the blades and the drum.
Description
VALVELESS BI-CHAMBER ROTARY STEAM ENGINE
WITH TURBINE EFFECT
BACRGROUND 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. Rowever, 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 characteri tic 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 tempera-ture 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 revolu-tion of a ~onventional steam engine is also l~mited 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 11799q,~;
steam engine in which internal pressures are compen-sated for and in which ~liding friction and wear are reduced which allows very efficient utilization of the expanding pressure force of a non-lubricated, pressur-ized medium as well as the kinetic energy of fastmoving 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 travellng gas molecules that impinge upon rotor blades as in conventional turbine.
The present invention includes an ou~er 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 ~wo sets 11~9946 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 i8 forced into each chamber at one side and i8 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. ~y 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 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 of 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. ~owever, as the rotational speed increases the amount of kinetic energy per revolution increa~es, 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 it~ 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. ~herefore, 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 120 to about 150C, especially geothermal applications, and due to its higher overall eficiencies it may supplant convention turbines in power plants. ~owever, 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 highl~ corrosive mediums due to the fact that high temperature resistant non-corrosive pla~tics can be used to construct this engine.
11'79946 Other objects, features, and characteristics of the present invention, as well as the methods and operation and function~ 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 ~pecification, 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 cross-sectional side view of the instant invention; and - FIWRE 2 shows a diagrammatic, top, cross-sectional 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, eliptical 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 11~9946 and 8 are diametrically opposed to one another and each pa$r is located on one side of the engine, as shown in Figure 1, and will service one side or port~on 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 13 includes a centrally mounted shaft 15 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 16 and 17 are also mounted. To insure proper sealing, packing rings 19 and 20 are inserted between disks 12 and 13 and hou~ing inserts 21 and 22, respectively.
The remaining portion of drum 9 is positioned ~
between rotor disks 12 and 13 and is comprised of a plurality of drum plates 23, 24, 25, 26, 27 and 28 rigidly mounted to and circumferentially spaced about disks ~2 and 13 80 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 sealins plate 29 so that two of such plates lie on oppo~ite side~ of each slot.
Rotatably mounted inside rotor disks 12 and 13 and adjacent the slots in drum 9 on ~ealed non-corrosive bearings 31 are six circular disks 30.
Four rigid bolts 52 extend outwardly from thesurface 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 S (not shown). Two sealing bars 33 and 34 are mounted on the side~ 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 50 a8 to extend lengthwise along the outside and the inside surface of each sealing b~r 33 and 34 such that a frictionless labyrinth sealinq 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 lenghthwise slots formed in their exterior surfaces or otherwise therebetween (not shown) create a frictionless labyrinth sealing effect at quch points.
The outer narrow surface 80 of rotor blades 35, 36, 37, 38, 39 and 40 also define between them-selves and the chambersl interior surface a plurality of length~ise extending slots ~not shown) whereby frictionless labyrinth sealing is also achieved between ~he ends of each rotor blade and the interior ~urface of the housing defining the radial chamber.
Thus, rotor blades 35, 36, ~7, 38, 39 and 40 will be 117~946 permitted to travel close to, but not in contact with the walls of radial chambers 10 and 11 while simul-taneously maintaining a seal with respect to the interior surface of the housing.
Sliding friction is prevented by having rotor blades 35, 36, 37, 3B, 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 Qhown in - 20 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 crank-shaft 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 non-corrosive bearings 48.
The other end 44 of crankshaft 82 is, inturn, mounted within rotor disk 13 through sealed non-corrosive bearing 53 so that disk 13 can rotate there-- around 80 that the rigid condition of crankshaft 82 remains, notwithstanding the rotation of drum 9 ~1~99g6 thereabout. To ease assembly, openings 49 are made in dlsks 12 and 13 as i8 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 ~ound generation.
Inlet ports 6 and 7, on the other~hand, lead to chambers 10 and 11 through maximum sized holes Sl where the medium will engage ro~or 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 under~tood 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.
WITH TURBINE EFFECT
BACRGROUND 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. Rowever, 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 characteri tic 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 tempera-ture 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 revolu-tion of a ~onventional steam engine is also l~mited 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 11799q,~;
steam engine in which internal pressures are compen-sated for and in which ~liding friction and wear are reduced which allows very efficient utilization of the expanding pressure force of a non-lubricated, pressur-ized medium as well as the kinetic energy of fastmoving 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 travellng gas molecules that impinge upon rotor blades as in conventional turbine.
The present invention includes an ou~er 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 ~wo sets 11~9946 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 i8 forced into each chamber at one side and i8 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. ~y 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 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 of 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. ~owever, as the rotational speed increases the amount of kinetic energy per revolution increa~es, 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 it~ 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. ~herefore, 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 120 to about 150C, especially geothermal applications, and due to its higher overall eficiencies it may supplant convention turbines in power plants. ~owever, 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 highl~ corrosive mediums due to the fact that high temperature resistant non-corrosive pla~tics can be used to construct this engine.
11'79946 Other objects, features, and characteristics of the present invention, as well as the methods and operation and function~ 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 ~pecification, 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 cross-sectional side view of the instant invention; and - FIWRE 2 shows a diagrammatic, top, cross-sectional 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, eliptical 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 11~9946 and 8 are diametrically opposed to one another and each pa$r is located on one side of the engine, as shown in Figure 1, and will service one side or port~on 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 13 includes a centrally mounted shaft 15 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 16 and 17 are also mounted. To insure proper sealing, packing rings 19 and 20 are inserted between disks 12 and 13 and hou~ing inserts 21 and 22, respectively.
The remaining portion of drum 9 is positioned ~
between rotor disks 12 and 13 and is comprised of a plurality of drum plates 23, 24, 25, 26, 27 and 28 rigidly mounted to and circumferentially spaced about disks ~2 and 13 80 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 sealins plate 29 so that two of such plates lie on oppo~ite side~ of each slot.
Rotatably mounted inside rotor disks 12 and 13 and adjacent the slots in drum 9 on ~ealed non-corrosive bearings 31 are six circular disks 30.
Four rigid bolts 52 extend outwardly from thesurface 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 S (not shown). Two sealing bars 33 and 34 are mounted on the side~ 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 50 a8 to extend lengthwise along the outside and the inside surface of each sealing b~r 33 and 34 such that a frictionless labyrinth sealinq 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 lenghthwise slots formed in their exterior surfaces or otherwise therebetween (not shown) create a frictionless labyrinth sealing effect at quch points.
The outer narrow surface 80 of rotor blades 35, 36, 37, 38, 39 and 40 also define between them-selves and the chambersl interior surface a plurality of length~ise extending slots ~not shown) whereby frictionless labyrinth sealing is also achieved between ~he ends of each rotor blade and the interior ~urface of the housing defining the radial chamber.
Thus, rotor blades 35, 36, ~7, 38, 39 and 40 will be 117~946 permitted to travel close to, but not in contact with the walls of radial chambers 10 and 11 while simul-taneously maintaining a seal with respect to the interior surface of the housing.
Sliding friction is prevented by having rotor blades 35, 36, 37, 3B, 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 Qhown in - 20 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 crank-shaft 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 non-corrosive bearings 48.
The other end 44 of crankshaft 82 is, inturn, mounted within rotor disk 13 through sealed non-corrosive bearing 53 so that disk 13 can rotate there-- around 80 that the rigid condition of crankshaft 82 remains, notwithstanding the rotation of drum 9 ~1~99g6 thereabout. To ease assembly, openings 49 are made in dlsks 12 and 13 as i8 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 ~ound generation.
Inlet ports 6 and 7, on the other~hand, lead to chambers 10 and 11 through maximum sized holes Sl where the medium will engage ro~or 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 under~tood 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 (21)
1. A displacement type rotary system turbine engine comprising:
- a housing having means defining a hollow, interior chamber formed from at least three aligned and intersecting partial cylindrical members;
- a stationary crankshaft mounted so as to extend across said hollow interior chamber, said crank-shaft having a central axis positioned at the center of said interior chamber and two separate outboard, eccen-trically positioned axes each spaced an equal predeter-mined distance from said central axis;
- drum means rotatably and concentrically mounted within said hollow interior chamber and about said stationary crankshaft for forming said hollow interior chamber into at least two diametrically opposed radial chambers;
- at least two sets of a plurality of seal-ing blades, each set being separately eccentrically and slidably mounted interiorly of said drum means about one of said outboard axes on said stationary crankshaft, each of said sets of blades rotating together with said drum means so that each of said at least two sets respectively rotate through a circular path and effect frictionless labyrinth sealing through only one of said at least two diametrically opposed radial chambers as said drum means rotates with each blade being radially movable therein;
- said housing further including inlet and outlet means for allowing entry and exit of a work-ing medium to each of said at least two radial chambers;
and - power take-off means operatively associat-ed 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.
- a housing having means defining a hollow, interior chamber formed from at least three aligned and intersecting partial cylindrical members;
- a stationary crankshaft mounted so as to extend across said hollow interior chamber, said crank-shaft having a central axis positioned at the center of said interior chamber and two separate outboard, eccen-trically positioned axes each spaced an equal predeter-mined distance from said central axis;
- drum means rotatably and concentrically mounted within said hollow interior chamber and about said stationary crankshaft for forming said hollow interior chamber into at least two diametrically opposed radial chambers;
- at least two sets of a plurality of seal-ing blades, each set being separately eccentrically and slidably mounted interiorly of said drum means about one of said outboard axes on said stationary crankshaft, each of said sets of blades rotating together with said drum means so that each of said at least two sets respectively rotate through a circular path and effect frictionless labyrinth sealing through only one of said at least two diametrically opposed radial chambers as said drum means rotates with each blade being radially movable therein;
- said housing further including inlet and outlet means for allowing entry and exit of a work-ing medium to each of said at least two radial chambers;
and - power take-off means operatively associat-ed 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 means includes at least one inlet port for each of said radial chambers to 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 sealing 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 with each of sealing blades positioned equidis-tantly about the circumference of said drum means.
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 further includes a plurality of separate sections secured so as to define a plurality of axially extending slots through which said sealing blades reciprocate and blade 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.
15. An engine as in claim 1, wherein thin slots are arranged lengthwise on the outermost surface of said sealing blade to effect the frictionless labyrinth sealing.
16. An engine as in claim 1, wherein said drum means includes means defining a plurality of pairs of diametrically opposed slots through which said blades slide and wherein the blades corresponding with each pair of diametrically opposed elongated slots are of different sets of blades.
17. An engine as in claim 1, wherein said drum means includes a plurality of drum plates that together define the exterior surface thereof and wherein a plura-lity of labyrinth slots extend about the exterior surface of said drum plates in a direction parallel to the axis of said drum means, said labyrinth slots serving to carry some of the partially expanded working medium over from the outlet port side to the inlet port side.
18. An engine as in claim 1, wherein the respective number of said radial chambers are arranged in diametrically opposed pairs and said sets of sealing blades comprise an uneven number of blades arranged so that each diametric alignment of sealing blades is comprised of two sealing blades belonging to a separate set.
19. A valveless rotary steam turbine engine comprising stationary engine housing having an interior chamber defined by a pair of opposing end walls and a continuous side wall, the side wall of which is defined by the intersection of at least three partial cylindrical members connected together to define a single interior chamber, the central axes of said partial cylindrical members being aligned so as to be parallel and lying in a common plane, with adjacent ones of said central axes being spaced apart by an equal, predetermined distance thereby defining the lines of intersection, a stationary crankshaft rigidly mounted in said interior chamber, a rotatably mounted drum-type rotor revolving concentrically about said crankshaft, at least one pair of diametrically opposed radial chambers defined by the side walls of said interior chamber and the outer surface of said drum-type rotor, said housing including means defining a plurality of diametrically situated inlet ports and outlet ports connecting with said radial chambers, said rotor including at least two separate sets of rotor blades rotatably mounted on corresponding eccentric parts of said crankshaft so that one set rotates about the outermost of said central axes and slidably mounted within said drum-type rotor, each of said sets of said rotor blades extending during at least a portion of each engine cycle into only one of said at least one pair of diametrically opposed radial chambers and wherein thin slots are arranged lengthwise on the outermost surface of said rotor blades and on the exterior surface of said drum plates to form friction-less labyrinth sealing with respect to the interior sur-faces of said engine housing.
20. An engine as in claim 19, wherein said rotor further includes two rotor disks, one having a central hub and the other having a central shaft for power output, said drum-type rotor further including a plurality of longitudinally extending drum plates rigidly interconnecting said rotor disks and evenly spaced apart about the circumference of said rotor thereby defining openings through said rotor blades move, sealing means rotatably mounted to said rotor to seal the movement of said blades within said openings.
21. An engine as in claim 20, wherein said sealing means comprises a plurality of circular disks rotatably mounted on each of said two rotor disks, a pair of spaced apart slidable sealing plates rotatably mounted within said opening between said rotor drum plates on opposite sides of and spaced from the rotor blade passing therethrough and a plurality of rotatably mounted sealing bars extending axially along said open-ings for rotatably engaging and for sealing between both said sealing plates and said rotor blades.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US21682080A | 1980-12-15 | 1980-12-15 | |
| US216,820 | 1980-12-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1179946A true CA1179946A (en) | 1984-12-27 |
Family
ID=22808636
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000391929A Expired CA1179946A (en) | 1980-12-15 | 1981-12-10 | Valveless bi-chamber rotary steam engine with turbine effect |
Country Status (12)
| Country | Link |
|---|---|
| JP (1) | JPS57124001A (en) |
| AR (1) | AR227343A1 (en) |
| AU (1) | AU7823381A (en) |
| BR (1) | BR8108112A (en) |
| CA (1) | CA1179946A (en) |
| DE (1) | DE3149040A1 (en) |
| ES (1) | ES8300929A1 (en) |
| FR (1) | FR2496162A1 (en) |
| GB (1) | GB2089893B (en) |
| IT (1) | IT1144536B (en) |
| SU (1) | SU1179938A3 (en) |
| ZA (1) | ZA818329B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2126282B (en) * | 1982-08-16 | 1985-11-13 | Robert Christian Groll | Rotary piston unit |
| DE102008010919A1 (en) | 2008-02-25 | 2009-09-03 | Markus Franssen | Waste recycling plant for the production of energy |
| DE102009014410A1 (en) | 2008-03-31 | 2009-10-01 | Etag Production Gmbh | Waste treatment plant for generating electric energy from combustion gases, has gasifier oven with upper, middle and lower section in connection with gas condenser, in connection with turbine module |
| DE102010026035A1 (en) * | 2010-07-03 | 2012-01-05 | Mahle International Gmbh | Rotary vane pump for brake booster in motor car, has chambers whose longitudinal ends are rotatably fixed in inner space along inner circumference trajectory, and roller bearing device provided at rotor in region of slot |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB475851A (en) * | 1936-03-18 | 1937-11-26 | Raoul Mabille | Improvements in or relating to rotary engines |
| US2713769A (en) * | 1949-07-21 | 1955-07-26 | Johnson John | Sliding vane rotary external combustion engine |
| FR1028123A (en) * | 1950-10-30 | 1953-05-19 | Rotary piston drive and operator machine | |
| GB795204A (en) * | 1955-07-20 | 1958-05-21 | Emi Ltd | Improvements in or relating to rotary oil vacuum pumps |
| US2903971A (en) * | 1957-05-27 | 1959-09-15 | Lowell J Collins | Pumps |
| FR1384755A (en) * | 1963-11-26 | 1965-01-08 | Rotary internal combustion engine | |
| FR1572729A (en) * | 1968-06-25 | 1969-06-27 | ||
| DE2355996A1 (en) * | 1973-11-09 | 1975-05-15 | Pfeiffer Vakuumtechnik | VALVE FOR ROTARY VALVE PUMPS |
| FR2272277A1 (en) * | 1974-05-24 | 1975-12-19 | Unus Dei F Lli Rossato V Et S | Rotary-piston air compressor - has sliders made from polyamide with spherical bronze powder charge and molybdenum disulphide |
| DE2436483A1 (en) * | 1974-07-29 | 1976-02-12 | Herzner Hans | INNER AXIS ROTATING PISTON MACHINE |
| US3952709A (en) * | 1974-10-23 | 1976-04-27 | General Motors Corporation | Orbital vane rotary machine |
-
1981
- 1981-11-24 GB GB8135361A patent/GB2089893B/en not_active Expired
- 1981-12-01 ZA ZA818329A patent/ZA818329B/en unknown
- 1981-12-03 AU AU78233/81A patent/AU7823381A/en not_active Abandoned
- 1981-12-10 CA CA000391929A patent/CA1179946A/en not_active Expired
- 1981-12-11 AR AR287780A patent/AR227343A1/en active
- 1981-12-11 DE DE19813149040 patent/DE3149040A1/en not_active Withdrawn
- 1981-12-14 JP JP56201449A patent/JPS57124001A/en active Pending
- 1981-12-14 BR BR8108112A patent/BR8108112A/en unknown
- 1981-12-14 IT IT49902/81A patent/IT1144536B/en active
- 1981-12-14 SU SU813365428A patent/SU1179938A3/en active
- 1981-12-14 ES ES507940A patent/ES8300929A1/en not_active Expired
- 1981-12-15 FR FR8123644A patent/FR2496162A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| FR2496162A1 (en) | 1982-06-18 |
| ES507940A0 (en) | 1982-11-01 |
| BR8108112A (en) | 1982-09-21 |
| AR227343A1 (en) | 1982-10-15 |
| SU1179938A3 (en) | 1985-09-15 |
| ZA818329B (en) | 1982-10-27 |
| IT1144536B (en) | 1986-10-29 |
| GB2089893B (en) | 1985-04-24 |
| AU7823381A (en) | 1982-06-24 |
| ES8300929A1 (en) | 1982-11-01 |
| GB2089893A (en) | 1982-06-30 |
| IT8149902A0 (en) | 1981-12-14 |
| JPS57124001A (en) | 1982-08-02 |
| DE3149040A1 (en) | 1982-10-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |