A vortex turbine and vortex-generating nozzle and a method of operation thereof

Abstract

Provided is a vortex turbine configured to produce mechanical torque or pressure including at least a cylindrical rotor housing; a fluid intake port; a first housing cap; a second housing cap; a first disk; an output coupler including a second disk and an output shaft; and a plurality of spiral rotor plates. Further provided is a convergent-divergent circular nozzle configured to produce a vortex fluid stream for input to the vortex turbine including at least a circular nozzle housing; a fluid intake port; a circular nozzle core; a shaft; a first flanged nut; a second flanged nut; and a spring.

Description

[0001] A VORTEX TURBINE AND VORTEX-GENERATING NOZZLE AND A METHOD OF

[0002] OPERATION THEREOF

[0003] FIELD

[0004] [1] The present disclosure generally relates to turbines and nozzles, and more specifically, to vortex turbines and vortex-generating nozzles.

[0005] BACKGROUND

[0006] [2] Turbo machinery, encompassing a range of devices including turbines, compressors, and pumps, plays a crucial role in numerous industrial applications due to its ability to convert energy between fluid and mechanical forms efficiently. Among the various types of turbines, vortex turbines are of particular interest due to their unique design principles and operational advantages.

[0007] [3] Vortex turbines operate on the principle of generating and harnessing vortex flows to produce rotational energy. Unlike traditional turbines that rely on axial or radial flow paths, vortex turbines utilize a swirling motion of fluid to transfer energy. This approach offers several advantages, including improved efficiency at variable flow rates and the ability to operate effectively in non-ideal flow conditions. The vortex motion in these turbines is typically induced by guiding the incoming fluid into a cylindrical or conical chamber, creating a stable, high-speed rotational flow. As the fluid spirals inward, its kinetic energy is converted into rotational energy, which can then be extracted by the vortex rotor connected to a generator or mechanical load. The simplicity of the design, with fewer moving parts and less susceptibility to fouling and wear, makes vortex turbines a reliable option for sustainable high efficiency and low maintenance rotary engine solutions.

[0008] [4] For instance, current prior art (see, US20020182054A 1) teaches a turbine converting a vortex stream of fluid blown parallel to a stack of disks of the turbine into mechanical torque, whereby the turbine induces drag due to the movement of the fluid being parallel to the disk surfaces. The resulting fluid-to-disk slippage prevents the turbine from performing with efficiency.

[0009] [5] A need exists for an improved vortex turbine design. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] [6] The accompanying drawings, which are incorporated herein and form a part of the specification, illustrate the present invention and, together with the description, further serve to explain the principles of the invention and to enable a person skilled in the pertinent art to make and use the invention.

[0011] [7] FIGS. 1A-1I illustrate an example of a vortex turbine and components thereof, according to some embodiments.

[0012] [8] FIGS. 2A-2E illustrate examples of spiral rotor plates of a vortex turbine, according to some embodiments.

[0013] [9] FIGS. 3A-3H illustrate an example of a vortex turbine including a vortex generator and components thereof, according to some embodiments.

[0014]

[0010] FIGS. 4A-4P illustrate an example of a vortex turbine and a vortex-generating convergent-divergent circular nozzle assembly and components thereof, according to some embodiments.

[0015]

[0011] FIGS. 5A-5D illustrate an example of a vortex-generating convergent-divergent circular nozzle, according to some embodiments.

[0016] SUMMARY

[0017]

[0012] The following presents a simplified summary of some embodiments of the techniques described herein in order to provide a basic understanding of the invention. This summary is not an extensive overview of the invention. It is not intended to identify key / critical elements of the invention or to delineate the scope of the invention. Its sole purpose is to present some embodiments of the invention in a simplified form as a prelude to the more detailed description that is presented below.

[0018]

[0013] Some embodiments provide a vortex turbine, including: a cylindrical rotor housing; a fluid intake port fixed to the cylindrical rotor housing, whereby a longitudinal axis of the fluid intake port is tangential to a longitudinal axis of the vortex turbine; a first housing cap coupled to the cylindrical rotor housing, sealing a first opening of the cylindrical rotor housing; a second housing cap coupled to the cylindrical rotor housing, at least partially covering a second opening of the cylindrical rotor housing, and including: a plate with a first through-hole positioned at a center of the plate; and a hollow cylinder concentrically aligned with the first through-hole; a first disk positioned within the cylindrical rotor housing; an output coupler positioned within the cylindrical rotor housing, and including: a second disk with a second through-hole positioned at a center of the second disk; and a hollow output shaft concentrically aligned with the second through-hole housed within the hollow cylinder; and a spiral rotor plates housed within the cylindrical rotor housing positioned between and fixed to at least one of the first disk and the second disk; wherein: the spiral rotor plates are arranged in a concentric spiral pattern, whereby a spiral rotor plate radii decreases from a periphery of the spiral rotor plates towards a center of the spiral rotor plates; the fluid intake port receives a high-pressure fluid stream injected into the cylinder housing; and the spiral rotor plates capture the high-pressure fluid stream injected into the cylinder housing through a plurality of openings staggered around the periphery of the spiral rotor plates, wherein: the high-pressure fluid stream moves in a circular path from the periphery of the spiral rotor plates towards the center of the spiral rotor plates, creating a vortex fluid stream; the high-pressure fluid stream contacts a surface of each of the spiral rotor plates at an angle, whereby the angle, and hence a pressure on the surface, increases as the high-pressure fluid stream moves towards the center of the spiral rotor plates; an angular speed of the high-pressure fluid stream increases as the high-pressure fluid stream moves towards the center of the spiral rotor plates, increasing centrifugal force acting on the high-pressure fluid stream and a build-up of pressure; and the pressure increases up to a level equal to a pressure of the high-pressure fluid stream received at the fluid intake port as the high-pressure fluid stream moves towards the center of the spiral rotor plates, resisting a flow of the high-pressure fluid stream and creating a resistive choke point, the resistance transferring rotational energy to the spiral rotor plates.

[0019]

[0014] Some embodiments provide a convergent-divergent circular nozzle and vortex turbine assembly, including: the convergent-divergent circular nozzle, including: a circular nozzle housing including a first through-hole on a first end and coupled on a second end to a first end of a cylindrical rotor housing of the vortex turbine; a fluid intake port fixed to the circular nozzle housing; a circular nozzle core housed within the circular nozzle housing and including a second through-hole; a shaft threaded on both ends and configured to pass through the first through-hole of the circular nozzle housing and the second through-hole of the circular nozzle core; a first flanged nut threaded onto a first end of the shaft; a spring configured to fit onto the shaft and positioned proximal to the second end of the shaft; and a second flanged nut threaded onto a second end of the shaft, whereby threading the second bolt to the second end of the shaft pre-loads the spring as the spring is compressed between the circular nozzle core and the second flanged nut; the vortex turbine, including: the cylindrical rotor housing; a housing cap coupled to the cylindrical rotor housing, at least partially covering a second opening of the cylindrical rotor housing, and including: a plate with a third through-hole positioned at a center of the plate; and a hollow cylinder concentrically aligned with the third through-hole; a first disk positioned within the cylindrical rotor housing; an output coupler positioned within the cylindrical rotor housing, and including: a second disk with a fourth through-hole positioned at a center of the second disk; and a hollow output shaft concentrically aligned with the fourth through-hole housed within the hollow cylinder; and spiral rotor plates housed within the cylindrical rotor housing positioned between and fixed to at least one of the first disk and the second disk; wherein: the spiral rotor plates are arranged in a concentric spiral pattern, whereby a spiral rotor plate radii decreases from a periphery of the spiral rotor plates towards a center of the spiral rotor plates; the fluid intake port receives a high-pressure fluid stream; the convergent-divergent circular nozzle generates a high-pressure vortex fluid stream; the spiral rotor plates capture the high-pressure vortex fluid stream through a plurality of openings staggered around the periphery of the spiral rotor plates, wherein: the high-pressure vortex fluid stream moves in a circular path from the periphery of the spiral rotor plates towards the center of the spiral rotor plates; the high-pressure vortex fluid stream contacts a surface of each of the spiral rotor plates at an angle, whereby the angle, and hence a pressure on the surface, increases as the high-pressure vortex fluid stream moves towards the center of the spiral rotor plates; an angular speed of the high-pressure vortex fluid stream increases as the high-pressure vortex fluid stream moves towards the center of the spiral rotor plates, increasing centrifugal force acting on the high-pressure vortex fluid stream and a build-up of pressure; and the pressure increases up to a level equal to a pressure of the high-pressure fluid stream received at the fluid intake port as the high-pressure vortex fluid stream moves towards the center of the spiral rotor plates, resisting a flow of the high-pressure fluid stream and creating a resistive choke point, the resistance transferring rotational energy to the spiral rotor plates; an inner surface of the circular nozzle housing and an outer surface of the circular nozzle core interface with one another, closing off any opening for fluid flow between them when no high-pressure fluid stream is received through the fluid intake port; the high-pressure fluid stream received through the fluid intake port causes the circular nozzle core to move away from the circular nozzle housing in a longitudinal direction of the shaft, compressing the spring and creating a constriction gap between the inner surface of the circular nozzle housing and the outer surface of the circular nozzle core; the constriction gap increases or decreases in size as the spring compresses or extends, respectively, based on a pressure of the high-pressure fluid stream; and the constriction gap is asymmetric and discontinuous around an internal periphery of the circular nozzle housing due to an asymmetrical shape of the circular nozzle core, causing the high-pressure fluid stream to be ejected from the circular nozzle as the high-pressure vortex fluid stream.

[0020] DETAILED DESCRIPTION

[0021]

[0015] The present invention will now be described in detail with reference to a few embodiments thereof as illustrated in the accompanying drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. It will be apparent, however, to one skilled in the art, that the present invention may be practiced without some or all of these specific details. In other instances, well known process steps and / or structures have not been described in detail in order to not unnecessarily obscure the present invention. Further, it should be emphasized that several inventive techniques are described, and embodiments are not limited to systems implementing all of those techniques, as various cost and engineering trade-offs may warrant systems that only afford a subset of the benefits described herein or that will be apparent to one of ordinary skill in the art.

[0022]

[0016] In the following detailed description of exemplary embodiments of the invention, reference is made to accompanying drawings (where like numbers represent like elements), which form a part hereof, and in which is shown by way of illustration specific exemplary embodiments in which the invention may be practiced. These embodiments are described in sufficient detail to enable those skilled in art to practice the invention, but other embodiments may be utilized, and logical, mechanical, electrical, and other changes may be made without departing from the scope of the present invention. The following detailed description is, therefore, not to be taken in a limiting sense.

[0023]

[0017] VORTEX TURBINE

[0024]

[0018] Embodiments provide a vortex turbine configured to produce a vortex fluid stream for generating mechanical torque or pressure. In embodiments, the vortex turbine includes a cylindrical rotor housing; a fluid intake port fixed to the cylindrical rotor housing, whereby a longitudinal axis of the fluid intake port is tangential to a longitudinal axis of the vortex turbine; a first housing cap coupled to the cylindrical rotor housing, sealing a first opening of the cylindrical rotor housing; a second housing cap coupled to the cylindrical rotor housing, at least partially covering a second opening of the cylindrical rotor housing, and including a plate with a first through-hole positioned at a center of the plate and a hollow cylinder concentrically aligned with the first through-hole; a first disk positioned within the cylindrical rotor housing; an output coupler positioned within the cylindrical rotor housing and including a second disk with a second through-hole positioned at a center of the second disk and a hollow output shaft concentrically aligned with the second through-hole housed within the hollow cylinder; and spiral rotor plates housed within the cylindrical rotor housing fixed to at least one of and positioned between the first disk and the second disk. In some embodiments, a first portion of the spiral rotor plates are fixed to the first disk and a second portion of the spiral rotor plates are fixed to the second disk, wherein the first and second portions of the spiral rotor plates are configured to interlace with one another to form an overall spiral pattern. Manufacturing the first portion of the spiral rotor plates fixed to the first disk and the second portion of the spiral rotor plates fixed to the second disk facilitates production. In some embodiments, the first disk, the output coupler, and the spiral rotor plates are manufactured as a single unit, wherein each end of each of the plurality of spital rotor plates are friction soldered to one of the first disk and the second disk.

[0025]

[0019] In embodiments where the objective is to generate mechanical torque, the vortex turbine further includes a plurality of bearings with inner races press fit onto the hollow output shaft and outer races press fit within the hollow cylinder to facilitate rotation of the spiral rotor plates and the first and second disks connected thereto around the longitudinal axis of the vortex turbine relative to the stationary cylindrical rotor housing and the first and second housing caps coupled thereto. In embodiments where the objective is to generate pressure, the spiral rotor plates and the first and second disks connected thereto are stationary.

[0026]

[0020] In embodiments, a high-pressure fluid stream is injected into the cylindrical rotor housing tangential to the longitudinal axis of the vortex turbine via the fluid intake port. The high-pressure compressible fluid stream may be in the form of a steam or a gas. The high-pressure fluid stream injected into the cylinder housing is captured by the spiral rotor plates through a plurality of openings staggered around a periphery of the spiral rotor plates. In embodiments, the spiral rotor plates are arranged in a concentric spiral pattern, with a decreasing spiral rotor plate radii towards a center of the concentric spiral pattern. The high-pressure fluid stream moves in a circular path from the periphery of the spiral rotor plates towards the center of the spiral rotor plates, creating a vortex fluid stream. As the fluid stream moves towards spiral rotor plates with incrementally decreasing spiral rotor plate radii, an angular speed of the fluid stream increases, causing an increasing centrifugal force acting on the fluid stream and a build-up of pressure. As the fluid stream moves towards the center of the spiral rotor plates, the pressure further increases up to a level equal to a pressure of the fluid stream at input, resisting the flow of the fluid stream and creating a resistive choke point. This resistance transfers rotational energy to the spiral rotor plates. If the spiral rotor plates and the first disk and the second disk to which the spiral rotor plates are fixed are allowed to spin, a speed of the fluid stream relative to the spiral rotor plates decreases and the choke point moves further towards an exhaust port (i.e., the hollow output shaft in this case). Operating near the choke point is where the most efficient energy conversion occurs. If the spiral rotor plates and the first disk and the second disk to which the spiral rotor plates are fixed are held stationary, a high pressure output is released through the exhaust port.

[0027]

[0021] The arrangement of the spiral rotor plates is such that the fluid stream is applied to a surface of a spiral rotor plate at an angle because of the continuous circular curve formed of the spiral rotor plates. The angle at which the fluid stream is applied to a surface of a spiral rotor plate increases as the fluid stream approaches the center of the spiral rotor plates, increasing a pressure on the surface of the spiral rotor plates as the fluid stream approaches the center of the spiral rotor plates. This helps reduce drag slippage between the fluid stream and the surface of the spiral rotor plate. The drag coefficient is directly dependent on a linear speed and an angular speed of the fluid stream, a fluid pressure, an area of contact between the fluid stream and the spiral rotor plates, an angle of contact of the fluid stream relative to a spiral rotor plate, a fluid weight, and a fluid density. A force of the fluid stream pulling the vortex turbine is proportional to the fluid speed, the fluid pressure, and the area of contact between the fluid stream and the spiral rotor plates. Adding additional spiral rotor plates to the vortex turbine increases the area of contact, thus increasing efficiency of a torque or a pressure conversion.

[0028]

[0022] In some embodiments, the spiral rotor plates have a logarithmic shape, such as the Golden or Fibonacci Spiral shape, to further compress the vortex fluid stream as it moves towards the center of the spiral rotor plates, thereby generating higher torque or pressure. The drag coefficient is directly dependent on the added compression coefficient resulting from the Fibonacci spiral shape. In some embodiments, the spiral rotor plates are arranged in a concentric spiral pattern, with a decreasing spiral rotor plate height towards a center of the spiral rotor plates, resulting in further compression of the fluid stream as the fluid stream approaches the center of the spiral rotor plates. In some embodiments, a spiral rotor plate height of a first set of the spiral rotor plates decreases from the periphery of the spiral rotor plates towards a radial mid-section of the spiral rotor plates, thereby converging the fluid stream, and a spiral rotor plate height of a second set of the spiral rotor plates increases from the radial mid-point of the spiral rotor plates to the center of the spiral rotor plates, thereby diverging the fluid stream. The decrease in spiral rotor plate height of the first set of the spiral rotor plates followed by the increase in spiral rotor plate height of the second set of spiral rotor plates creates a constriction point for conversion-diversion. The converging-diverging effect converts pressure to kinetic energy which increases the angular speed of the fluid stream, and hence, centrifugal force, thereby increasing efficiency. Each of these methods may be used individually or in combination to help compress the fluid stream sooner.

[0029]

[0023] The vortex turbine may be used for, for example, motor applications in the transportation, manufacturing, and hydroelectric industries or as a compressor for refrigeration and heat pump applications.

[0024] In embodiments, at least a portion of the vortex turbine is fabricated of a durable material (e.g., metal). In some embodiments, one or more components of the vortex turbine are fabricated of metal alloy or ceramic that can withstand high temperatures for higher power applications.

[0030]

[0025] FIGS. 1A andlB illustrate exploded and assembled views of an example embodiment of a vortex turbine 100 and FIGS. 1C-1I illustrate components thereof. The vortex turbine 100 includes a cylindrical rotor housing 101 ; a fluid intake port 102 fixed to the cylindrical rotor housing 101, whereby a longitudinal axis 103 of the fluid intake port 102 is tangential to a longitudinal axis 104 of the vortex turbine 100; a first housing cap 105 coupled to the cylindrical rotor housing 101, sealing a first opening 106 of the cylindrical rotor housing 101; a second housing cap 107 coupled to the cylindrical rotor housing 101, at least partially covering a second opening 108 of the cylindrical rotor housing 101, and including a plate 109 with a first through-hole 110 positioned at a center of the plate 109 and a hollow cylinder 111 concentrically aligned with the first through- hole 110; a first disk 112 positioned within the cylindrical rotor housing 101; an output coupler 113 positioned within the cylindrical rotor housing 101 and including a second disk 114 with a second through-hole 115 positioned at a center of the second disk 114 and a hollow output shaft 116 concentrically aligned with the second through-hole 115 housed within the hollow cylinder 111; and spiral rotor plates 117 including a first portion 118a and second portion 118b of the spiral rotor plates 117 housed within the cylindrical rotor housing 101. The first portion 118a of the spiral rotor plates 117 are fixed to the first disk 112 and the second portion 118b of the spiral rotor plates 117 are fixed to the second disk 114, wherein the first and second portions 118a and 118b of the spiral rotor plates 117 are configured to interlace with one another. The first housing cap 105 and the rotor housing 101 include fastening tabs 119 and 120, respectively, that align with and fasten to one another. The second housing cap 107 and the rotor housing 101 include fastening tabs 121 and 122, respectively, that align with and fasten to one another.

[0031]

[0026] FIGS. 2 A and 2B illustrate spiral rotor plates 200 fixed to a disk 201 and arranged in a concentric spiral pattern, with a decreasing spiral rotor plate radii towards a center of the spiral rotor plates 200 and a plurality of openings 202 staggered around a periphery 203 of the spiral rotor plates 200. FIG. 2C illustrates the spiral rotor plates 200 arranged in a concentric spiral patern, with a decreasing spiral rotor plate height towards a center 204 of the spiral rotor plates 200. FIGS. 2D and 2E illustrate an alternative embodiment wherein a spiral rotor plate height of a first set 205 of spiral rotor plates 200 decreases from the periphery 203 of the spiral rotor plates 200 towards a radial mid-section 206 of the spiral rotor plates 200. A spiral rotor plate height of a second set 207 of the spiral rotor plates 200 increases from the radial mid-section 206 of the spiral rotor plates 200 towards the center 204 of the spiral rotor plates 200. The decrease in the spiral rotor plate height of the first set 205 of the spiral rotor plates 200 followed by the increase in the spiral rotor plate height of the second set 207 of spiral rotor plates 200 creates a constriction point, shown by constriction line 208, for conversion-diversion of the high-pressure fluid stream, increasing the angular speed and centrifugal force of the high-pressure fluid stream.

[0032]

[0027] VORTEX TURBINE WITH IMPELLER DRIVEN VORTEX GENERATOR

[0033]

[0028] In some embodiments, the vortex turbine is connected to a vortex generator that generates a high-pressure vortex fluid stream captured by the spiral rotor plates. In such a case, the fluid intake port is omited and rather than including the first housing cap for sealing the first end of the cylindrical rotor housing (as is shown in FIGS. 1 A andlB), the vortex generator is coupled to the first end of the cylindrical rotor housing. In some embodiments, the vortex generator includes a cylindrical impeller housing coupled on a first end to the first end of the cylindrical rotor housing; an impeller housed within the impeller housing for generating the high-pressure vortex fluid stream; a motor housing coupled on a first end to a second end of the impeller housing; a motor housed within the motor housing including an output shaft coupled to the impeller; and a motor bracket coupled to the motor and a second end of the motor housing. In some embodiments, the second housing cap and the rotor housing include fastening tabs that align with and fasten to one another. In some embodiments, the impeller housing and the rotor housing include fastening tabs that align with and fasten to one another. In some embodiments, the impeller housing and the motor housing include fastening tabs that align with and fasten to one another. In some embodiments, the motor bracket is fastened to fastening tabs of the motor housing. In some embodiments, the motor includes an electric motor. In embodiments, the impeller is driven at a very high RPM via the motor to generate the high-pressure vortex fluid stream, which is then captured by the spiral rotor plates. In embodiments, air is received as input through openings in the impeller housing.

[0034]

[0029] In some embodiments, one or more components of the vortex turbine and / or the impeller driven vortex generator are fabricated of metal alloy or ceramic that can withstand high temperatures for higher power applications.

[0035]

[0030] FIGS. 3A and3B illustrate exploded and assembled views of an example embodiment of a vortex turbine 300a and a vortex generator 300b and FIGS. 3C-3H illustrate components thereof. The vortex turbine 300a includes a cylindrical rotor housing 301; a housing cap 302 coupled to the cylindrical rotor housing 301, at least partially covering an opening 303 of the cylindrical rotor housing 301, and including a plate 304 with a first through-hole 305 positioned at a center of the plate 304 and a hollow cylinder 306 concentrically aligned with the first through-hole 305; a first disk 307 positioned within the cylindrical rotor housing 301; an output coupler 308 positioned within the cylindrical rotor housing 301 and including a second disk 309 with a second through-hole 310 positioned at a center of the second disk 309 and a hollow output shaft 311 concentrically aligned with the second through-hole 310 housed within the hollow cylinder 306; and spiral rotor plates 312 and 313 housed within the cylindrical rotor housing 301 positioned between the first disk 307 and the second disk 309 and each fixed to one of the first disk 307 and the second disk 309. A first portion of the spiral rotor plates 312 are fixed to the first disk 307 and a second portion of the spiral rotor plates 313 are fixed to the second disk 309, wherein the first and second portions of the spiral rotor plates 312 and 313 are configured to interlace with one another to form an overall a spiral pattern. The vortex generator 300b includes a cylindrical impeller housing 314 coupled on a first end to the first end of the cylindrical rotor housing 301; an impeller 315 housed within the impeller housing 314; a motor housing 316 coupled on a first end to a second end of the impeller housing 314; a motor 317 housed within the motor housing 316 including an output shaft 318 coupled to the impeller 315; and a motor bracket 319 coupled to the motor 317 and a second end of the motor housing 316. The housing cap 302 and the rotor housing 301 include fastening tabs 320 and 321, respectively, that align with and fasten to one another. The impeller housing 314 and the rotor housing 301 include fastening tabs 322 and 323, respectively, that align with and fasten to one another. The motor housing 316 includes fastening tabs 324 that fasten to a flange 325 of the impeller housing 314 one another. The motor bracket 319 is fastened to a flange 326 of the motor housing 316. The impeller housing 314 includes air intake openings 327 for drawing air in during operation.

[0036]

[0031] VORTEX TURBINE WITH VORTEX-GENERATING CONVERGENT- DIVERGENT CIRCULAR NOZZLE

[0037]

[0032] In some embodiments, the vortex turbine connects with a convergent-divergent circular nozzle that generates a high-pressure vortex fluid stream captured by the spiral rotor plates. In such a case, the fluid intake port fixed to the cylindrical rotor housing is omitted and rather than including the first housing cap for sealing the first end of the cylindrical rotor housing (as is shown in FIGS. 1 A and IB), the circular nozzle is coupled to the first end of the cylindrical rotor housing. In some embodiments, the convergent- divergent circular nozzle includes a circular nozzle housing including a first through-hole on a first end and coupled on a second end to the first end of the cylindrical rotor housing; a fluid intake port fixed to the circular nozzle housing; a circular nozzle core housed within the circular nozzle housing and including a second through-hole; a shaft threaded on both ends and configured to pass through the first through-hole of the circular nozzle housing and the second through-hole of the circular nozzle core; a first flanged nut threaded onto a first end of the shaft; a spring configured to fit onto the shaft and positioned proximal to the second end of the shaft; a second flanged nut threaded onto a second end of the shaft, whereby threading the second bolt to the second end of the shaft pre-loads the spring as the spring is compressed between the circular nozzle core and the second flanged nut. In some embodiments, the circular nozzle housing and the rotor housing include fastening tabs that align with and fasten to one another. In some embodiments, the second housing cap and the rotor housing include fastening tabs that align with and fasten to one another.

[0038]

[0033] When no fluid stream is provided as input to the convergent-divergent circular nozzle, an inner surface of the circular nozzle housing and an outer surface of the circular nozzle core interface with one another, closing olf any opening for fluid to flow between the two components. When a high-pressure fluid stream is provided through the fluid intake port, the pressure from the high-pressure fluid stream causes the circular nozzle core to move away from the circular nozzle housing, in a longitudinal direction of the shaft, compressing the spring and creating a constriction gap between the inner surface of the circular nozzle housing and the outer surface of the circular nozzle core. The constriction gap, controlled by the spring, creates a throttling mechanism, whereby as the pressure from the injected high-pressure fluid stream increases, the constriction gap also increases. The circular nozzle core is limited to motion along the longitudinal axis of the shaft, and thereby the vortex turbine, and slides fore and aft along the spring-loaded shaft to accommodate different fluid pressures received through the fluid intake port. As the spring force of the retained circular nozzle core is overcome by the fluid pressure of the injected fluid stream, the constriction gap starts to open asymmetrically and discontinuously around an internal periphery of the circular nozzle housing due to an asymmetrical shape of the circular nozzle core, causing the high-pressure fluid stream to be ej ected from the circular nozzle as a high- pressure vortex fluid stream (i.e., in a circular vortex pattern) towards the spiral rotor plates. The high-pressure fluid stream injected through the fluid intake port follows a path of least resistance within the circular nozzle housing. The high-pressure fluid stream escapes through the constriction gap along the path of least resistance, the path flowing to the right or the left as a frontal / axial direction has a higher fluid flow resistance. In some embodiments, a guide tab is disposed in the circular nozzle housing to preset a direction of rotation of the vortex stream.

[0039]

[0034] In some embodiments, one or more components of the vortex turbine and / or the vortex-generating convergent-divergent circular nozzle are fabricated of metal alloy or ceramic that can withstand high temperatures for higher power applications.

[0040]

[0035] FIGS. 4A and 4B illustrate exploded and assembled views of an example embodiment of a vortex turbine 400a and a convergent-divergent circular nozzle 400b and FIGS. 4C-4P illustrate components thereof. Some components are shown as translucent for the purpose of viewing components of the vortex turbine and the convergent-divergent circular nozzle that would otherwise be hidden. The vortex turbine 400a includes a cylindrical rotor housing 401; a housing cap 402 coupled to the cylindrical rotor housing 401, at least partially covering an opening 403 of the cylindrical rotor housing 401, and including a plate 404 with a first through-hole 405 positioned at a center of the plate 404 and a hollow cylinder 406 concentrically aligned with the first through-hole 405; a first disk 407 positioned within the cylindrical rotor housing 401; an output coupler 408 positioned within the cylindrical rotor housing 401 and including a second disk 409 with a second through-hole 410 positioned at a center of the second disk 409 and a hollow output shaft 411 concentrically aligned with the second through-hole 410 housed within the hollow cylinder 406; and spiral rotor plates 412 and 413 housed within the cylindrical rotor housing 401 positioned between the first disk 407 and the second disk 409 and each fixed to one of the first disk 407 and the second disk 409. A first portion of the spiral rotor plates 412 are fixed to the first disk 407 and a second portion of the spiral rotor plates 413 are fixed to the second disk 409, wherein the first and second portions of the spiral rotor plates 412 and 413 are configured to interlace with one another to form an overall spiral pattern. The circular nozzle 400b includes a circular nozzle housing 414 including a first through- hole 415 on a first end and coupled on a second end to the first end of the cylindrical rotor housing 401; a fluid intake port 416 fixed to the circular nozzle housing 414; a circular nozzle core 417 housed within the circular nozzle housing 414 and including a second through-hole 418; a shaft 419 threaded on both ends and configured to pass through the first through-hole 415 of the circular nozzle housing 414 and the second through-hole 418 of the circular nozzle core 417; a first flanged nut 420 threaded onto a first end of the shaft 419; a spring 421 configured to fit onto the shaft 419 and positioned proximal to the second end of the shaft 419; a second flanged nut 422 threaded onto a second end of the shaft 419, whereby threading the second flanged nut 422 to the second end of the shaft 419 pre-loads the spring 421 as the spring 421 is compressed between the circular nozzle core 417 and the second flanged nut 422. The circular nozzle housing 414 and the rotor housing 401 include fastening tabs 423 and 424, respectively, that align with and fasten to one another. The housing cap 402 and the rotor housing 401 include fastening tabs 425 and 426, respectively, that align with and fasten to one another. The first disk 407 and the spiral rotor plates 412 may be manufactured as a singular component. The output coupler 408 and the spiral rotor disks 413 may be manufactured as a singular component.

[0041]

[0036] FIG. 4P illustrates a constriction gap 427 created when pressure from a high- pressure fluid stream causes the circular nozzle core 417 to move away from the circular nozzle housing 414, in a longitudinal direction of the shaft 419, compressing the spring 421 and creating the constriction gap 427 between an inner surface of the circular nozzle housing 414 and an outer surface of the circular nozzle core 417.

[0037] FIG. 5 A illustrates an example of a vortex-generating convergent-divergent circular nozzle including similar components and operating similarly to the vortex-generating convergent-divergent circular nozzle illustrated in FIG. 4P. For instance, included is a circular nozzle housing 500; a fluid intake port 501; a circular nozzle core 502 housed within the circular nozzle housing 500; a shaft 503 threaded on both ends; a first flanged nut 504 threaded onto a first end of the shaft 503; a spring 505 configured to fit onto the shaft 503 and positioned proximal to the second end of the shaft 503; a second flanged nut 506 threaded onto a second end of the shaft 503, whereby threading the second flanged nut 506 to the second end of the shaft 503 pre-loads the spring 505 as the spring 505 is compressed between the circular nozzle core 502 and the second flanged nut 506. The vortex-generating convergent-divergent circular nozzle further includes a fuel input 507 from a fuel burning chamber and a guide tab 508 for initializing a direction of the high- pressure vortex fluid stream 509 towards a desired side. FIGS. 5B-5D illustrate a constriction gap 510 created when pressure from the high-pressure fluid stream causes the circular nozzle core 502 to move away from the circular nozzle housing 500, in a longitudinal direction of the shaft 503, compressing the spring 505 and creating the constriction gap 510 between an inner surface of the circular nozzle housing 500 and an outer surface of the circular nozzle core 502. In FIGS. 5B and 5C, constriction points 511a- 511d, fluid passage profdes 512a-512d, location of convergence-divergence 513, and compression input area 514 are shown. In a frontal direction 515, fluid passage profdes, such as 512a-512c, have less distance before reaching their respective constriction point, therefore, the fluid flow resistance is very high in the frontal direction 515. The more the fluid passage profde is offset towards the side 516, the further the distance to their respective constriction point and the lower the fluid flow resistance is. For example, FIG.5C illustrates a distance 517 to the constriction point 5 lid of fluid passage profde 512d. The high-pressure fluid stream follows the fluid passage profde 512d as it corresponds to the path of least fluid flow resistance, wrapping around the circular nozzle core 502 and creating the high-pressure vortex fluid stream 509. This pushes following high-pressure fluid stream input towards the same fluid passage profde 512d, creating the high-pressure vortex fluid stream 509. The direction of the vortex stream generated may be directed towards the left or right side, as set using guide tab 508.

[0038] The principal aspect of the convergent-divergent circular nozzle embodiments described herein is the constriction gap created between the inner surface of the circular nozzle housing and the outer surface of the circular nozzle core around the circumference of the circular nozzle core. The constriction gap has a profde of convergence-divergence around the circumference of the circular nozzle core. The constriction gap is controlled by the spring, wherein the pressure from the high-pressure fluid stream causes the circular nozzle core to move away from the circular nozzle housing via compression of the spring, thereby forming the constriction gap. As such, the convergence-divergence constriction gap is variable.

[0042]

[0039] It should be understood that the various embodiments described herein are presented by way of example, and that numerous variations, modifications, or combinations of the described embodiments may be made without departing from the scope of the invention. In some instances, certain features of one embodiment may be used in combination with features of another embodiment, or multiple embodiments may be integrated together to achieve a desired result. Additionally, certain elements or steps of the described embodiments may be omitted, substituted, or altered depending on the specific implementation or application.

[0043]

[0040] In various embodiments, certain components, methods, or functionalities described herein may be modified or adapted to fit specific use cases or design constraints. These modifications may be made in view of particular user requirements, environmental conditions, or regulatory considerations.

[0044]

[0041] Alternative configurations of the embodiments described herein are also possible. In some cases, a particular feature described with reference to one embodiment may be utilized in other embodiments, even if not explicitly mentioned. Similarly, the order of steps in a process / method or the arrangement of components in a system or apparatus may be altered, provided that the underlying principles of the invention are maintained.

[0045]

[0042] While particular embodiments have been described, it is to be understood that alternative embodiments may be employed in place of the specifically described forms. In some cases, specific components may be replaced with functionally equivalent alternatives, and in others, operational steps may be rearranged or omitted, all without departing from the spirit and scope of the invention.

Claims

CLAIMS1. A vortex turbine, compri sing : a cylindrical rotor housing; a fluid intake port fixed to the cylindrical rotor housing, whereby a longitudinal axis of the fluid intake port is tangential to a longitudinal axis of the vortex turbine; a first housing cap coupled to the cylindrical rotor housing, sealing a first opening of the cylindrical rotor housing; a second housing cap coupled to the cylindrical rotor housing, at least partially covering a second opening of the cylindrical rotor housing, and comprising: a plate with a first through-hole positioned at a center of the plate; and a hollow cylinder concentrically aligned with the first through-hole; a first disk positioned within the cylindrical rotor housing; an output coupler positioned within the cylindrical rotor housing, and comprising: a second disk with a second through-hole positioned at a center of the second disk; and a hollow output shaft concentrically aligned with the second through-hole housed within the hollow cylinder; and spiral rotor plates housed within the cylindrical rotor housing positioned between and each fixed to at least one of the first disk and the second disk; wherein: the spiral rotor plates are arranged in a concentric spiral pattern, whereby a spiral rotor plate radii decreases from a periphery of the spiral rotor plates towards a center of the spiral rotor plates; the fluid intake port receives a high-pressure fluid stream injected into the cylinder housing; and the spiral rotor plates capture the high-pressure fluid stream injected into the cylinder housing through a plurality of openings staggered around the periphery of the spiral rotor plates, wherein: the high-pressure fluid stream moves in a circular path from the periphery of the spiral rotor plates towards the center of the spiral rotor plates, creating a vortex fluid stream;the high-pressure fluid stream contacts a surface of each of the spiral rotor plates at an angle, whereby the angle, and hence a pressure on the surface, increases as the high-pressure fluid stream moves towards the center of the spiral rotor plates; an angular speed of the high-pressure fluid stream increases as the high-pressure fluid stream moves towards the center of the spiral rotor plates, increasing centrifugal force acting on the high-pressure fluid stream and a build-up of pressure; and the pressure increases up to a level equal to a pressure of the high- pressure fluid stream received at the fluid intake port as the high- pressure fluid stream moves towards the center of the spiral rotor plates, resisting a flow of the high-pressure fluid stream and creating a resistive choke point, the resistance transferring rotational energy to the spiral rotor plates.

2. The vortex turbine of claim 1, wherein: the spiral rotor plates and the first disk and the second disk to which the spiral rotor plates are fixed are free to rotate around the longitudinal axis of the vortex turbine; a speed of the high-pressure fluid stream relative to the spiral rotor plates decreases and the choke point moves towards an exhaust port; and the exhaust port comprises the hollow output shaft.

3. The vortex turbine of claim 1, wherein: the spiral rotor plates, the first disk, and the second disk are held stationary; a high pressure output is released through an exhaust port; and the exhaust port comprises the hollow output shaft.

4. The vortex turbine of claim 1, further comprising a plurality of bearings, wherein: inner races of the each of the plurality of bearings are press fit onto the hollow output shaft and outer races of the each of the plurality of bearings are press fit within the hollow cylinder; and the plurality of bearings facilitates rotation of the spiral rotor plates and the first and second disks connected thereto around the longitudinal axis of the vortex turbine relative to the cylindrical rotor housing and the first and second housing caps coupled thereto.

5. The vortex turbine of claim 1, wherein: a spiral rotor plate height of a first set of the spiral rotor plates decreases from the periphery of the spiral rotor plates towards a radial mid-section of the spiral rotor plates; the first set of spiral rotor plates comprises spiral rotor plates positioned between the periphery of the spiral rotor plates and the radial mid-section of the spiral rotor plates; a spiral rotor plate height of a second set of the spiral rotor plates increases from the radial mid-section of the spiral rotor plates towards the center of the spiral rotor plates; the second set of the spiral rotor plates comprises spiral rotor plates positioned between the radial mid-section of the spiral rotor plates and the center of the spiral rotor plates; and the decrease in the spiral rotor plate height of the first set of the spiral rotor plates followed by the increase in the spiral rotor plate height of the second set of spiral rotor plates creates a constriction point for conversion-diversion of the high-pressure fluid stream, increasing the angular speed and centrifugal force of the high-pressure fluid stream.

6. The vortex turbine of claim 1, wherein a spiral rotor plate height decreases from the periphery of the spiral rotor plates towards the center of the spiral rotor plates.

7. The vortex turbine of claim 1, wherein at least one of: the spiral rotor plates are arranged in a Fibonacci spiral shape; and a spiral rotor plate height decreases from the periphery of the spiral rotor plates towards the center of the spiral rotor plates.

8. The vortex turbine of claim 1, wherein: a first portion of the spiral rotor plates are fixed to the first disk and a second portion of the spiral rotor plates are fixed to the second disk; and the first and second portions of the spiral rotor plates are configured to interlace with one another to form the concentric spiral pattern.

9. The vortex turbine of claim 1, wherein at least one of: the first disk, the output coupler, and the spiral rotor plates are manufactured as a single unit; and at least a portion of the vortex turbine is fabricated of metal.

0. A convergent-divergent circular nozzle and vortex turbine assembly, comprising: the convergent-divergent circular nozzle, comprising: a circular nozzle housing comprising a first through-hole on a first end and coupled on a second end to a first end of a cylindrical rotor housing of the vortex turbine; a fluid intake port fixed to the circular nozzle housing; a circular nozzle core housed within the circular nozzle housing and comprising a second through-hole; a shaft threaded on both ends and configured to pass through the first through- hole of the circular nozzle housing and the second through-hole of the circular nozzle core; a first flanged nut threaded onto a first end of the shaft; a spring configured to fit onto the shaft and positioned proximal to the second end of the shaft; and a second flanged nut threaded onto a second end of the shaft, whereby threading the second bolt to the second end of the shaft pre-loads the spring as the spring is compressed between the circular nozzle core and the second flanged nut; and the vortex turbine, comprising: the cylindrical rotor housing; a housing cap coupled to the cylindrical rotor housing, at least partially covering a second opening of the cylindrical rotor housing, and comprising: a plate with a third through-hole positioned at a center of the plate; and a hollow cylinder concentrically aligned with the third through-hole; a first disk positioned within the cylindrical rotor housing; an output coupler positioned within the cylindrical rotor housing, and comprising: a second disk with a fourth through-hole positioned at a center of the second disk; and a hollow output shaft concentrically aligned with the fourth through- hole housed within the hollow cylinder; andspiral rotor plates housed within the cylindrical rotor housing positioned between and each fixed to at least one of the first disk and the second disk; wherein: the spiral rotor plates are arranged in a concentric spiral pattern, whereby a spiral rotor plate radii decreases from a periphery of the spiral rotor plates towards a center of the spiral rotor plates; the fluid intake port receives a high-pressure fluid stream; the convergent-divergent circular nozzle generates a high-pressure vortex fluid stream; the spiral rotor plates capture the high-pressure vortex fluid stream through a plurality of openings staggered around the periphery of the spiral rotor plates, wherein: the high-pressure vortex fluid stream moves in a circular path from the periphery of the spiral rotor plates towards the center of the spiral rotor plates; the high-pressure vortex fluid stream contacts a surface of each of the spiral rotor plates at an angle, whereby the angle, and hence a pressure on the surface, increases as the high-pressure vortex fluid stream moves towards the center of the spiral rotor plates; an angular speed of the high-pressure vortex fluid stream increases as the high-pressure vortex fluid stream moves towards the center of the spiral rotor plates, increasing centrifugal force acting on the high- pressure vortex fluid stream and a build-up of pressure; and the pressure increases up to a level equal to a pressure of the high- pressure fluid stream received at the fluid intake port as the high- pressure vortex fluid stream moves towards the center of the spiral rotor plates, resisting a flow of the high-pressure fluid stream and creating a resistive choke point, the resistance transferring rotational energy to the spiral rotor plates; an inner surface of the circular nozzle housing and an outer surface of the circular nozzle core interface with one another, closing off any opening forfluid flow between them when no high-pressure fluid stream is received through the fluid intake port; the high-pressure fluid stream received through the fluid intake port causes the circular nozzle core to move away from the circular nozzle housing in a longitudinal direction of the shaft, compressing the spring and creating a constriction gap between the inner surface of the circular nozzle housing and the outer surface of the circular nozzle core; the constriction gap increases or decreases in size as the spring compresses or extends, respectively, based on a pressure of the high-pressure fluid stream; and the constriction gap is asymmetric and discontinuous around an internal periphery of the circular nozzle housing due to an asymmetrical shape of the circular nozzle core, causing the high-pressure fluid stream to be ejected from the circular nozzle as the high-pressure vortex fluid stream.

11. The assembly of claim 10, wherein the convergent-divergent circular nozzle further comprises a guide tab disposed in on a periphery of the circular nozzle housing to preset a direction of rotation of the high-pressure vortex fluid stream.

12. The assembly of claim 10, wherein: the spiral rotor plates and the first disk and the second disk to which the spiral rotor plates are fixed are free to rotate around the longitudinal axis of the vortex turbine; a speed of the high-pressure vortex fluid stream relative to the spiral rotor plates decreases and the choke point moves towards an exhaust port; and the exhaust port comprises the hollow output shaft.

13. The assembly of claim 10, wherein: the spiral rotor plates, the first disk, and the second disk are held stationary; a high pressure output is released through an exhaust port; and the exhaust port comprises the hollow output shaft.

14. The assembly of claim 10, wherein the vortex turbine further comprises a plurality of bearings, wherein: inner races of the each of the plurality of bearings are press fit onto the hollow output shaft and outer races of the each of the plurality of bearings are press fit within the hollow cylinder; andthe plurality of bearings facilitates rotation of the spiral rotor plates and the first and second disks connected thereto around the longitudinal axis of the vortex turbine relative to the cylindrical rotor housing and the first and second housing caps coupled thereto.

15. The assembly of claim 10, wherein: a spiral rotor plate height of a first set of the spiral rotor plates decreases from the periphery of the spiral rotor plates towards a radial mid-section of the spiral rotor plates; the first set of spiral rotor plates comprises spiral rotor plates positioned between the periphery of the spiral rotor plates and the radial mid-section of the spiral rotor plates; a spiral rotor plate height of a second set of the spiral rotor plates increases from the radial mid-section of the spiral rotor plates towards the center of the spiral rotor plates; the second set of the spiral rotor plates comprises spiral rotor plates positioned between the radial mid-section of the spiral rotor plates and the center of the spiral rotor plates; and the decrease in the spiral rotor plate height of the first set of the spiral rotor plates followed by the increase in the spiral rotor plate height of the second set of spiral rotor plates creates a constriction point for conversion-diversion of the high-pressure fluid stream, increasing the angular speed and centrifugal force of the high-pressure fluid stream.

16. The assembly of claim 10, wherein a spiral rotor plate height decreases from the periphery of the spiral rotor plates towards the center of the spiral rotor plates.

17. The assembly of claim 10, wherein at least one of: the spiral rotor plates are arranged in a Fibonacci spiral shape; and a spiral rotor plate height decreases from the periphery of the spiral rotor plates towards the center of the spiral rotor plates.

18. The assembly of claim 10, wherein: a first portion of the spiral rotor plates are fixed to the first disk and a second portion of the spiral rotor plates are fixed to the second disk; and the first and second portions of the spiral rotor plates are configured to interlace with one another to form the concentric spiral pattern.

19. The assembly of claim 10, wherein the first disk, the output coupler, and the spiral rotor plates are manufactured as a single unit.

20. The assembly of claim 10, wherein at least a portion of the assembly is fabricated of metal.

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