Vortex Tube Supplying Superheated Vapor for Turbine Power Generation

Abstract

The vortex tube when properly used within a Rankine cycle can produce phenomenal results. This invention functionally describes the preferred vortex tube used to produce superheated vapor from a compressed heated liquid without summoning the additional heat required for latent-heat to effect vaporization. The vortex tube provides superheated vapor to a turbine for generating electricity burning 50% less fossil fuel, also releasing 50% less carbon emissions to the environment. The vortex tube extends the efficient Rankine Cycle temperature range well below 150 F. with the proper refrigerant choice. The physical size and function of the hearing equipment is reduced. The invention delivers new thermal efficiencies for both the Rankine Cycle and the Organic Rankine Cycle.

Claims

1. A process of making a superheated vapor from a compressed liquid comprising the steps: entering at least one inlet tangentially a compressed liquid stream into the internal diameter and near perpendicular of a cylindrical inlet chamber, said compressed liquid stream transverses at least one inlet, reducing the liquid temperature and pressure, creating a second duel-phase fluid stream having fluid expanding and straight line acceleration; said second duel-phase fluid stream following the inlet chamber internal diameter forcing a duel-phase fluid rotation developing a fluid vortex and vital angular momentum, also straight line forward and angular acceleration, initiating both a fluid temperature and pressure reduction, said second duel-phase fluid stream at least partially converting its pressure energy into the accelerating rotating fluid kinetic energy, forming a condensate precipitating out of said accelerating rotating fluid, emitting condensation heat, forming and migrating condensate inward due to a loss of angular momentum and inward toward a lower pressure developing near the vortex center, sweeping away residual liquid water and condensate by a passing swirling center counterflow vortex in close proximity, said inlet chamber having two outlets enables continuing fluid flow forward and exiting said inlet chamber and said vortex tube; absorbs an abandoned condensation heat left behind with a wet accelerating rotating vapor, said wet accelerating rotating vapor becomes heated, creating a rotating heated vapor stream, absorbing the condensation heat into said rotating heated vapor stream to accelerate angularly said rotating heated vapor stream, allowing a reduction in the spin diameter of said rotating heated vapor stream while maintaining near the same angular momentum, said rotating heated vapor stream being pushed forward by an entry pressure differential into the inlet chamber and afterwards into a smaller internal diameter tube, leaving the most liquid behind in the inlet chamber to convert into vapor; said rotating heated vapor stream entering said smaller internal diameter tube, creating a hot rotating vapor stream increasing the kinetic energy, said hot rotating vapor stream temperature and pressure both decrease, said decreasing pressure creates a pressure gradient that pushes stream flow forward to said hot rotating vapor stream; said hot rotating vapor stream expands by reducing the vapor pressure and absorbing the abandoned condensation heat, said hot rotating vapor stream velocity accelerates angularly about a rotating axis and in a straight line forward, with condensate forms, precipitates-out, because of the loss of angular momentum while emitting condensation heat, discharging condensate and sweeping away the condensate by said swirling center counterflow vortex passing in close proximity, said hot rotating vapor stream absorbing the condensation heat left behind, creating a superheated vapor stream migrating outward, because of the gain of angular momentum by absorbing condensation heat, the difference in angular momentum separates the two energies, a hot superheated vapor stream continuing to expand until reaching the end of the tube, precipitating condensate and absorbing condensation heat, said hot superheated vapor stream becoming hotter migrating outward gathering on the outer edge of said hot rotating vapor stream next to a tube internal diameter wall, allowing only this hot superheated vapor outer edge to pass the tube end, valving control regulating mass flow to balance the volume flow rates of liquid and vapor components, with the remaining hot rotating vapor stream being deflected back, reversing the remaining flow stream and forming said swirling center counterflow vortex continuing backward exiting the inlet chamber outlet and exiting said vortex tube.

2. The process of claim 1 wherein said compressed liquid stream is a heated non-boiling compressed liquid stream.

3. The process of claim 1 wherein at least one inlet is at least one nozzle.

4. The process of claim 1 wherein said vortex tube is a vortex steam generator.

5. A process comprising the steps of: providing an inlet chamber internal diameter that is equal to said tube internal diameter, both being said tube without said inlet chamber impediment; absorbing the abandoned condensation by said rotating heated vapor stream as heat accelerates angularly, creating a hot rotating vapor stream increasing the kinetic energy, diminishing the pressure gradient to push said hot rotating vapor stream axially forward, decreasing said hot rotating vapor stream temperature and pressure, expanding said hot rotating vapor stream by reducing vapor pressure and absorbing said abandoned condensation heat; accelerating the angular velocity of said hot rotating vapor stream about a rotating axis and in a straight line forward, continuing to form condensate, precipitating-out, and emitting condensation heat, discharging condensate and sweeping away the condensate by said swirling center counterflow vortex passing in close proximity, absorbing said hot rotating vapor stream with the condensation heat left behind, creating a superheated vapor stream migrating outward, continuing to expand a hot superheated vapor stream until reaching the end of the tube, precipitating condensate and absorbing condensation heat, and, heating said hot superheated vapor stream and migrating outward gathering on the outer edge of said hot rotating vapor stream, covering the tube internal diameter wall, allowing only said hot superheated vapor covering to pass the tube end. cm 6. A system that provides a superheated vapor from a compressed liquid comprising: an inlet chamber having at least one entry inlet receiving a first compressed liquid stream tangentially and near perpendicular to the cylindrical internal diameter of said inlet chamber; said inlet chamber having at least one inlet producing a second straight line compressed liquid stream passing through at least one inlet reducing said second straight line compressed liquid stream temperature and pressure, changing state creating a third duel-phase fluid stream exhibiting fluid expansion and acceleration; said inlet chamber internal diameter forcing said third duel-phase fluid stream to rotate developing a fourth rotating duel-phase vortex stream, said inlet chamber forced rotation changing both fluid temperature and pressure of said third duel-phase fluid stream developing said fourth rotating duel-phase vortex stream decreasing temperature and pressure, exhibiting expansion and angular acceleration, causing condensate separation by loss of condensate angular momentum, while maintaining the balance with the angular momentum gain of the rotating vapor, precipitating out of said fourth rotating duel-phase vortex stream, emitting condensation heat; said inlet chamber condensate forms and migrates inward due to a loss of angular momentum caused by loss of heat and inward toward a lower pressure developing near the vortex center, said inlet chamber having two outlets of particular size, first outlet for continuing forward in said vortex tube and the second outlet for exiting said vortex tube, said inlet chamber residual liquid water and condensate are swept away by a swirling center counterflow vortex exiting the second outlet and exiting said vortex tube; said fifth rotating vapor absorbs an abandoned condensation heat left behind, said fifth rotating vapor becomes heated, creating a sixth rotating heated vapor stream, said sixth rotating heated vapor stream migrating outward due to a gain of angular momentum caused by a gain of heat, while maintaining a balance in angular momentum with said condensate; said inlet chamber transitioning from said cylindrical internal diameter to said first outlet presents an impediment for moving forward the angular stream flow, said inlet chamber said sixth rotating heated vapor stream increasing angular acceleration allowing a reduction in the spin diameter of said sixth rotating heated vapor stream in order to exit said inlet chamber through particular reduced internal diameter of said first outlet, said inlet chamber said sixth rotating heated vapor stream changing state, creating a seventh hot rotating vapor stream exhibiting vapor expansion and angular acceleration being pushed forward by said entry pressure differential from said inlet chamber into said first outlet of smaller internal diameter, leaving the most liquid behind in said inlet chamber farther converting into vapor or for disposal, said first outlet releasing said seventh hot rotating vapor stream exhibiting vapor expansion and angular acceleration pushing forward into a tube; said tube receiving said seventh hot rotating vapor stream pushing forward decreasing temperature and pressure, forming a condensate precipitating out of said seventh hot rotating vapor stream, emitting condensation heat; said tube condensate precipitating and migrating inward due to a loss of angular momentum caused by loss of heat and inward toward a lower pressure developing near the tube vortex center, said tube said seventh hot rotating vapor stream migrating outward due to a gain of angular momentum caused by a gain of heat, while maintaining a balance in angular momentum with said tube condensate; said tube condensate is swept away by said swirling center counterflow vortex exiting the second outlet and exiting said vortex tube; said seventh hot rotating vapor stream absorbing the condensation heat left behind, said seventh hot rotating vapor stream becoming heated, creating an eighth dryer and superheated vapor stream, said eighth dryer and superheated vapor stream continuing to expand pushing forward until reaching the end of said tube, precipitating condensate and absorbing condensation heat, said eighth dryer and superheated vapor stream becoming hotter gathering on the outer edge of said seventh hot rotating vapor stream, said tube end allowing only said eighth dryer and superheated vapor stream gathering on the outer edge to pass the tube end continuing forward for farther use; said tube end causing said seventh hot rotating vapor stream to be deflected back reversing the flow stream forming said swirling center counterflow vortex, said tube swirling counterflow vortex continuing backward collecting precipitating condensate and releasing at least additional condensation heat for absorbing, said tube swirling counterflow vortex continuing backward exiting the second outlet and exiting said vortex tube.

7. The apparatus according to claim 6 wherein at least one inlet is at least one nozzle.

8. The apparatus according to claim 6 wherein first compressed liquid stream is a first heated non-boiling compressed liquid stream.

9. The apparatus according to claim 6 wherein a vortex tube is a vortex steam generator.

10. The apparatus according to claim 6 wherein said first outlet internal diameter is equal to the cylindrical internal diameter of said inlet chamber; said tube internal diameter is smaller than or near equal to the internal diameter of the cylindrical internal diameter of said inlet chamber.

11. A process for providing a superheated vapor from a liquid stream comprising the steps of: providing a first liquid stream; increasing the pressure of a first liquid stream; providing a first compressed liquid stream; heating said first compressed liquid stream in a first heat exchanger, said first heat exchanger producing a second non-boiling compressed liquid stream that has a higher temperature than said first compressed liquid stream, said first heat exchanger receiving heat from a first external heat source; providing said second non-boiling compressed liquid stream to a vortex tube to separate said second compressed non-boiling liquid stream into a second cool fluid stream and a hot second superheated vapor stream, without additional heat from an external heat source; providing said hot second superheated vapor stream from said vortex tube for use.

12. The process of claim 11 further comprising the steps of: heating said first compressed liquid stream to a non-boiling temperature, without boiling said second non-boiling compressed liquid stream, until said second non-boiling compressed liquid stream temperature is near liquid saturation temperature and below for that compressing pressure.

13. The process of claim 11 wherein liquid stream is a liquid water stream.

14. The process of claim 11 wherein vapor stream is a steam stream.

15. The process of claim 11 wherein a first heat exchanger is a shell and plate heat exchanger.

16. The process of claim 11 wherein a first heat exchanger is absent and said first compressed liquid stream is provided as a second non-boiling compressed liquid stream from an external heat source, and provided directly to said vortex tube.

17. The process of claim 11 wherein said first heat exchanger produces a second non-boiling compressed liquid stream that has a higher temperature than said first compressed liquid stream, said first heat exchanger receiving heat from a first external heat source; and said first vortex tube receiving said second non-boiling compressed liquid stream being segregated in said first vortex tube into a hot second superheated vapor stream and a second sub-cooled liquid stream, a first turbine receives said hot second superheated vapor stream for use.

18. The process of claim 11 wherein liquid stream is a liquid water stream.

19. The process of claim 11 wherein vapor stream is a steam stream.

20. The process of claim 11 wherein a first heat exchanger is a shell and plate heat exchanger.

21. The process of claim 11 wherein a first heat exchanger is absent and said first compressed liquid stream is provided as a second non-boiling compressed liquid stream from an external heat source, and provided to said vortex tube.

22. The process of claim 11 wherein said first heat exchanger heating said first compressed liquid stream to a non-boiling temperature; said first heat exchanger heating said second non-boiling compressed liquid stream until said second non-boiling compressed liquid stream temperature is near liquid saturation temperature and below for that particular compressing pressure.

Description

DESCRIPTION OF DRAWINGS

[0082] FIG. 1 is a process map of a conventional liquid refrigerant flashing process.

[0083] FIG. 2 is a process map of a heatless liquid refrigerant flashing process.

[0084] FIG. 3 is a process map of a conventional steam power plant water flashing process.

[0085] FIG. 4 is a process map of a steam power plant heatless water flashing process.

[0086] FIG. 5 is a schematic design of rudimentary Rankine Cycle with vortex tube.

[0087] FIG. 6 is a schematic design Rankine Cycle with vortex tube and economizer.

[0088] FIG. 7 is a schematic design Rankine Cycle with two vortex tubes and two turbines.

[0089] FIG. 8 is a schematic design Rankine Cycle with two vortex tubes and two turbines and economizer.

[0090] FIG. 9 is a schematic design Rankine Cycle with two feed pumps, two vortex tubes, and two liquid heaters.

[0091] FIG. 10 is a schematic design Rankine Cycle with two feed pumps, two vortex tubes, two liquid heaters, and economizer

DETAILED DESCRIPTION OF THE INVENTION

[0092] The present invention is directed to a process for creating a supercritical vapor from a subcooled liquid without adding the latent-heat to effect the vaporization of the subcooled liquid. At its beginning state, subcooled liquid is pumped into the vaporizing heat exchanger to add heat. The process flow control ensures the pressurized subcooled liquid remains a subcooled liquid as heat is continually added. The heat transferred to raise the temperature of the subcooled liquid produces a hot subcooled liquid near the saturated liquid inlet temperature. With respect to these conditions, the vortex tube separation process of a subcooled liquid assures the production of two outflows: 1) a supercritical vapor stream and 2) a subcooled liquid stream. The supercritical vapor stream continues routing with the process, and the subcooled liquid stream, while returning to its beginning state for further cycling, retains a residual energy as well as a value for cooling.

[0093] The present invention shown in FIG. 2 is a schematic map depicting the Hardgrave process for vaporizing a subcooled liquid refrigerant stream: [0094] 1) pump the subcooled liquid refrigerant stream to the desired pressure; [0095] 2) provide the pressurized subcooled liquid stream into a heat exchanger; [0096] 3) transfer heat from an external heat source to the pressurized subcooled liquid stream passing through the heat exchanger raising the stream temperature, but not vaporizing the liquid stream, until the stream temperature is near the saturated liquid inlet temperature for the desired pressure; [0097] 4) feed this hot pressurized subcooled liquid stream into a conventional counter-flow vortex tube to separate the hot pressurized subcooled liquid stream into two outflows: [0098] a) a cool subcooled liquid stream and [0099] b) the desired supercritical refrigerant vapor stream, without the addition of Latent Heat.

[0100] The supercritical refrigerant vapor stream created by the vortex tube has developed a higher temperature state than the saturated liquid inlet temperature; [0101] 5) provide the supercritical refrigerant vapor stream to convert the heat energy into a work, electrical or motive force.

[0102] The supercritical vapor exhaust stream and the cool subcooled liquid stream are mixed resulting in a cool mixture stream returning to their original state for further cycling.

[0103] The invention shown is the rudimentary Rankine Cycle with vortex tube 120. FIG. 5 is the basic schematic design for a heatless flashing process used to produce electrical power. It is the starting point for all of the five following schematic designs.

[0104] The present invention shown in FIG. 5, is a schematic design depicting the Hardgrave process for vaporizing the subcooled liquid refrigerant stream 112 to produce electricity: [0105] use feed pump 100 to pump the subcooled liquid refrigerant stream 101 to the desired pressure; [0106] flow the pressurized subcooled liquid stream 102 into a heat exchanger 110; [0107] transfer heat from an external heat source to the subcooled liquid stream 102 to raise its temperature, but not vaporize the subcooled liquid stream 102, until stream 102 temperature is near the saturated liquid inlet temperature for the desired pressure; feed this hot subcooled liquid stream 112 into the inlet of a conventional counter-flow vortex tube 120 to separate the hot subcooled liquid stream 112 into two outflows: a cool subcooled liquid stream 122; and the desired supercritical refrigerant vapor stream 123, without the addition of Latent Heat. The supercritical refrigerant vapor stream 123 is provided at a higher temperature than the saturated liquid inlet temperature and the supercritical refrigerant vapor stream 123 is used to drive a turbine 130 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0108] The subcooled liquid stream 122 retains a residual energy and value for cooling while returning to its state of beginning for further cycling. The cool subcooled liquid stream 122 is fed into a Joule-Thomson device 160 emerging with lower temperature and pressure as feed stream 162. The temperature and pressure of stream 123 is lowered when it emerges from the turbine 130 as supercritical vapor feed stream 132 which is mixed with the cool subcooled liquid feed stream 162, yielding a cool mixed stream 172 that is fed into a condenser 170. Emerging as the condensed subcooled liquid refrigerant stream 101 that is transmitted from the condenser 170 at a lower temperature, and is fed into pump 100, the place of beginning, completing the cycle.

[0109] This invention shown is the same as the rudimentary Rankine Cycle with vortex tube 220, FIG. 5, with the addition of an economizing heat exchanger 285. FIG. 6, is a schematic design depicting the Hardgrave process for vaporizing the subcooled liquid refrigerant stream 212 to produce electricity: use feed pump 200 to pump the subcooled liquid refrigerant stream 201 to a desired pressure; feed the pressurized subcooled liquid stream 202 into an economizing heat exchanger 285 to be pre-heated; and flow the pre-heated pressurized subcooled liquid stream 282 into the heat exchanger 210. The pre-heating process reduces the amount of heat transferred from an external heat source thereby improving the heat efficiency.

[0110] Continuing the process, transfer heat from an external heat source to the pre-heated pressurized subcooled liquid stream 282 raising the stream 282 temperature, but not to the state of vaporizing the liquid stream 242, but only until the liquid stream 242 temperature is near the saturated liquid inlet temperature for the desired pressure; feed this hot pressurized subcooled liquid stream 212 into the inlet of a conventional counter-flow vortex tube 220 to separate the hot pressurized subcooled liquid stream 212 into two outflows: a cool subcooled liquid stream 222; and the desired supercritical refrigerant vapor stream 223, without the addition of Latent Heat.

[0111] The supercritical refrigerant vapor stream 223 is provided at a higher temperature than the saturated liquid inlet temperature and the supercritical refrigerant vapor stream 223 is used to drive the turbine 230 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0112] The cool subcooled liquid stream 222 is fed into a Joule-Thomson device 260, emerging with lower temperature and pressure as feed stream 262. The temperature and pressure of stream 223 is lowered when it emerges from the turbine 230 as supercritical vapor feed stream 232.

[0113] Feed stream 232 is transmitted from the turbine 230 as a supercritical vapor into the economizing heat exchanger 285 to provide the heat for pre-heating the pressurized subcooled liquid stream 202. The temperature of supercritical vapor feed stream 232 is lowered when it emerges from the economizing heat exchanger 285 as feed stream 284.

[0114] Feed stream 284 is mixed with feed stream 262, resulting in a cooler mixed stream 272 that is fed into a condenser 270. The condensed subcooled liquid refrigerant stream 201 is transmitted from the condenser 270 at a lower temperature, and is fed into pump 200, the place of beginning, completing the cycle.

[0115] The invention shown is the same as the rudimentary Rankine Cycle with vortex tube 320, FIG. 5, with an alteration of the cool subcooled liquid return stream's 322 use rather than just returning to its state of beginning for further cycling. This invention is designed to use its residual energy before the return of the subcooled liquid stream 322 by adding a second vortex tube 330 and turbine 350.

[0116] FIG. 7, is a schematic design depicting the Hardgrave process for vaporizing the supercritical liquid refrigerant stream 312 to produce electricity: use feed pump 300 to pump the subcooled liquid refrigerant stream 301 to the desired pressure; provide the pressurized subcooled liquid stream 302 into a heat exchanger 310; transfer heat from an external heat source to the pressurized subcooled liquid stream 302 to raise its temperature, but not vaporize the liquid stream 302, until stream 302 temperature is near the saturated liquid inlet temperature for the desired pressure; feed this hot pressurized subcooled liquid stream 312 into the inlet of a first conventional counter-flow vortex tube 320 to separate the hot pressurized subcooled liquid stream 312 into two outflows: a first cool subcooled liquid stream 322; and the desired first supercritical refrigerant vapor stream 323, without the addition of Latent Heat.

[0117] The first supercritical refrigerant vapor stream 323 is provided at a higher temperature by the vortex tube 320 than the saturated liquid inlet temperature for the desired pressure; [0118] provide the first supercritical refrigerant vapor stream 323 to drive a turbine 340 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0119] Feed the first cool subcooled liquid stream 322 into the inlet of a second conventional counter-flow vortex tube 330 to separate the first cool subcooled liquid stream 322 into a second cool subcooled liquid stream 332; and the second supercritical refrigerant vapor stream 333, without the addition of Latent Heat.

[0120] The electric power output of second turbine 350 can also be increased minutely if the pressure of the first cool subcooled liquid stream 322 is increased by a second liquid feed pump 390 (not shown) prior to being fed into a second conventional counter-flow vortex tube 330.

[0121] The second supercritical refrigerant vapor stream 333 is provided at a higher temperature than the saturated liquid inlet temperature for its chosen pressure, provide the second supercritical refrigerant vapor stream 333 to drive a turbine 350 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0122] The second cool subcooled liquid stream 332 is fed into a Joule-Thomson device 360 emerging with lower temperature and pressure as feed stream 362. The temperature and pressure of stream 323 is lowered when it emerges from the turbine 340 in feed stream 342. The temperature and pressure of stream 333 is lowered when it emerges from the turbine 350 in feed stream 352. Feed streams 352 and feed stream 362 are mixed forming feed stream 373, which is mixed with feed stream 342, the combined stream 372 is transmitted into the a condenser 370. The condensed subcooled liquid refrigerant stream 301 is transmitted from the condenser 370 at a lower temperature, and is fed into pump 300, the place of beginning, completing the cycle.

[0123] The invention shown as FIG. 8, is the same as the rudimentary Rankine Cycle with vortex tube 420, FIG. 9, with the addition of an economizing heat exchanger 485 and an alteration of the cool subcooled liquid return stream 422.

[0124] There are two positions for the addition of an economizing heat exchanger 485. The position chosen is between the feed pump 400 and the heat exchanger 410 to pre-heat the pressurized subcooled liquid stream 402 before being introduced into the heat exchanger 410. This position for the pre-heating process reduces the amount of heat transferred from an external heat source, thereby improving the heat efficiency.

[0125] The alternate position for the addition of an economizing heat exchanger 485 is between the first conventional counter-flow vortex tube 420 and the second conventional counter-flow vortex tube 430 to pre-heat the first cool subcooled liquid stream 422 before being introduced into the inlet of the second conventional counter-flow vortex tube 430. This position for the pre-heating process increases the power output of the second turbine 450 not chosen.

[0126] The altered use of the cool subcooled liquid return stream 422 is to produce power, by adding a second vortex tube 430 and a second turbine 450, from the cool subcooled liquid return stream 422 residual energy, rather than just returning to its state of beginning for further cycling, as shown in this invention.

[0127] FIG. 8, is a schematic design depicting the Hardgrave process for vaporizing a pressurized subcooled liquid refrigerant stream 412 to produce electricity: use feed pump 400 to pump the subcooled liquid refrigerant stream 401 to a desired pressure; provide the pressurized subcooled liquid stream 402 into an economizing heat exchanger 485 to be pre-heated and provide a pre-heated pressurized subcooled liquid stream 482 into a heat exchanger 410; transfer heat from an external heat source into the pressurized subcooled liquid stream 482 to raise the temperature, but not vaporize the liquid stream 482, until stream 482 temperature is near the saturated liquid inlet temperature for the desired pressure; provide this hot pressurized subcooled liquid stream 412 into the inlet of a first conventional counter-flow vortex tube 420 to separate the hot pressurized subcooled liquid stream 412 into two outflows: a first cool subcooled liquid stream 422; and the desired first supercritical refrigerant vapor stream 423, without the addition of Latent Heat. The first supercritical refrigerant vapor stream 423 is provided at a higher temperature than the saturated liquid inlet temperature for the desired pressure and the first supercritical refrigerant vapor stream 423 is used to drive a turbine 440 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0128] Feed the first cool subcooled liquid stream 422 into the inlet of a second conventional counter-flow vortex tube 430 to separate the first cool subcooled liquid stream 422 into two outflows: a second cool subcooled liquid stream 432; and the second supercritical refrigerant vapor stream 433, without the addition of Latent Heat. The second supercritical refrigerant vapor stream 433 is provided at a higher temperature than the saturated liquid inlet temperature for its chosen pressure; provide the second supercritical refrigerant vapor stream 433 to drive a turbine 450 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0129] The second cool subcooled liquid stream 432 is fed into a Joule-Thomson device 460 emerging with lower temperature and pressure as feed stream 462. The temperature and pressure of stream 423 is lowered when it emerges from the turbine 440 in feed stream 442, The temperature and pressure of stream 433 is lowered when it emerges from the turbine 450 in feed stream 452 which is mixed with feed stream 442.

[0130] The combined stream 483 is transmitted from the turbines 440 and 450 as a supercritical vapor into the economizing heat exchanger 485 to provide the heat for pre-heating the pressurized subcooled liquid stream 402. The temperature of feed stream 483 is lowered when it emerges from the economizing heat exchanger 485 as feed stream 484.

[0131] Feed stream 484 is combined with feed stream 462, the combined stream 472 is fed into a condenser 470. The condensed subcooled liquid refrigerant stream 401 is transmitted from the condenser 470 at a lower temperature, and is fed into pump 400, the place of beginning, completing the cycle.

[0132] The invention shown as FIG. 9, is the same as the rudimentary Rankine Cycle with vortex tube 520, as shown by FIG. 5, with the altered use of the cool subcooled liquid return stream 522. The altered use of the cool subcooled liquid return stream 522 residual energy is to produce power rather than just returning to its state of beginning for further cycling.

[0133] By adding a second vortex tube 530, and a second turbine 550, as shown in FIG. 3, there is a modest increase in power output. If a second feed pump 590 is added, only a minute increase in power is seen. Only after a second heat exchanger 580 is added, a significant increase in power is noted.

[0134] FIG. 9 is a schematic design depicting the Hardgrave process for vaporizing a pressurized subcooled liquid refrigerant stream 512 to produce electricity: use feed pump 500 to pump the subcooled liquid refrigerant stream 501 to a desired pressure; provide the pressurized subcooled liquid stream 502 into a heat exchanger 510; transfer heat from an external heat source into the pressurized subcooled liquid stream 502 to raise the stream temperature, but not vaporize the liquid stream 502, until stream 502 temperature is near the saturated liquid inlet temperature for the desired pressure; provide this hot pressurized subcooled liquid stream 512 into the inlet of a first conventional counter-flow vortex tube 520 to separate the hot compressed liquid stream 512 into two outflows: a first cool subcooled liquid stream 522; and the desired first supercritical refrigerant vapor stream 523, without the addition of Latent Heat. The first supercritical refrigerant vapor stream 523 is provided at a higher temperature than the saturated liquid inlet temperature for the desired pressure and the first supercritical refrigerant vapor stream 523 is used to drive a turbine 540 to produce electricity or convert the heat energy into a work, electrical or motive force. Feed the first cool subcooled liquid stream 522 into second feed pump 590 to pump the subcooled liquid refrigerant stream 522 to a desired pressure; provide the pressurized subcooled liquid stream 592 into a second heat exchanger 580; re-heat the subcooled liquid stream 592 to raise the stream temperature, but not vaporize the liquid stream 592, until stream 592 temperature is near the saturated liquid inlet temperature for the desired pressure; provide this hot pressurized subcooled liquid stream 582 into the inlet of a second conventional counter-flow vortex tube 530 to separate the hot subcooled liquid stream 582 into two outflows: a second cool subcooled liquid stream 532; and the desired second supercritical refrigerant vapor stream 533, without the addition of Latent Heat. The second supercritical refrigerant vapor stream 533 is provided at a higher temperature than the saturated liquid inlet temperature for the desired pressure, and the second supercritical refrigerant vapor stream 533 is used to drive a turbine 550 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0135] The second cool subcooled liquid stream 532 is fed into a Joule-Thomson device 560 emerging with lower temperature and pressure as feed stream 562. The temperature and pressure of stream 523 is lowered when it emerges from the turbine 540 in feed stream 542. The temperature and pressure of stream 533 is lowered when it emerges from the turbine 550 in feed stream 552. Feed streams 552 and feed stream 562 are mixed forming feed stream 573, which is mixed with feed stream 542, the combined stream 572 is transmitted into the condenser 570. The condensed subcooled liquid refrigerant stream 501 is transmitted from the condenser 570 at a lower temperature, and is fed into inlet of pump 500, the place of beginning, completing the cycle.

[0136] The invention shown as FIG. 10, is the same as the rudimentary Rankine Cycle with vortex tube 620, as shown by FIG. 5, with the addition of an economizing heat exchanger 685 and an alteration of the cool subcooled liquid return stream 622.

[0137] There are two positions for the addition of an economizing heat exchanger 685. The position chosen is between the feed pump 600 and the heat exchanger 610 to pre-heat the pressurized subcooled liquid stream 602 before being introduced into the heat exchanger 610. This position for the pre-heating process reduces the amount of heat transferred from an external heat source, thereby improving the heat efficiency.

[0138] The alternate position for the addition of an economizing heat exchanger 485 is between the second feed pump 690 and the second conventional counter-flow vortex tube 630 replacing the second heat exchanger 680 to pre-heat the first cool subcooled liquid stream 622 before being introduced into the second conventional counter-flow vortex tube 630. This position for the pre-heating process increases the power output of the second turbine 650 without additional heat from an external heat source.

[0139] The altered use of the cool subcooled liquid return stream 622 is to produce power by adding a second vortex tube 630 and a turbine 650, from the cool subcooled liquid return stream 622 residual energy, rather than just returning to its state of beginning for further cycling, as shown in this invention.

[0140] By adding a second vortex tube 630, and a second turbine 650, as shown in FIG. 3, there is a modest increase in power output. If a second feed pump 690 is added, only a minute increase in power is seen. Only after a second heat exchanger 680 is added, a significant increase in power is noted.

[0141] FIG. 10, is a schematic design depicting the Hardgrave process for vaporizing a pressurized subcooled liquid refrigerant stream 612 to produce electricity: use feed pump 600 to pump the subcooled liquid refrigerant stream 601 to a desired pressure; provide the pressurized subcooled liquid stream 602 into an economizing heat exchanger 685 to be pre-heated; and provide a pre-heated pressurized compressed liquid stream 682 into a heat exchanger 610. Transfer heat from an external heat source into the subcooled liquid stream 682 to raise the temperature, but not vaporize the liquid stream 682, until stream 682 temperature is near the saturated liquid inlet temperature for the desired pressure.

[0142] Provide this hot pressurized subcooled liquid stream 612 into the inlet of a first conventional counter-flow vortex tube 620 to separate the hot subcooled liquid stream 612 into two outflows: a first cool subcooled liquid stream 622; and the desired first supercritical refrigerant vapor stream 623, without the addition of Latent Heat. The first supercritical refrigerant vapor stream 623 is provided at a higher temperature than the saturated liquid inlet temperature for the desired pressure. Provide the first supercritical refrigerant vapor stream 623 to drive a turbine 640 to produce electricity or convert the heat energy into a work, electrical or motive force. Feed the first cool subcooled liquid stream 622 into a second feed pump 690 to pump the subcooled liquid refrigerant stream 622 to a desired pressure. Provide the pressurized subcooled liquid stream 692 into a second heat exchanger 680, re-heat the subcooled liquid stream 692 to raise the temperature, but not vaporize the liquid stream 692, until stream 692 temperature is near the saturated liquid inlet temperature for the desired pressure.

[0143] Provide this hot pressurized subcooled liquid stream 686 into the inlet of a second conventional counter-flow vortex tube 630 to separate the hot subcooled liquid stream 686 into two outflows: a second cool subcooled liquid stream 632; and the desired second supercritical refrigerant vapor stream 633, without the addition of Latent Heat. The second supercritical refrigerant vapor stream 633 is provided at a higher temperature than the saturated liquid inlet temperature for the desired pressure and the second supercritical refrigerant vapor stream 633 is used to drive a turbine 650 to produce electricity or convert the heat energy into a work, electrical or motive force.

[0144] The second cool subcooled liquid stream 632 is fed into a Joule-Thomson device 660 emerging with lower temperature and pressure as feed stream 662. The temperature and pressure of stream 623 is lowered when it emerges from the turbine 640 in feed stream 642. The temperature and pressure of stream 633 is lowered when it emerges from the turbine 650 in feed stream 652 which is mixed with feed stream 642.

[0145] The combined stream 683 is transmitted from the turbines 640 and 650 as a supercritical vapor into the economizing heat exchanger 685 to provide the heat for pre-heating the pressurized subcooled liquid stream 602. The temperature of feed stream 683 is lowered when it emerges from the economizing heat exchanger 685 as feed stream 684.

[0146] Feed stream 684 is combined with feed stream 662, the combined stream 672 is fed into a condenser 670. The condensed subcooled liquid refrigerant stream 601 is transmitted from the condenser 670 at a lower temperature, and is fed into pump 600, the place of beginning, completing the cycle.

[0147] The particular embodiments disclosed above are illustrative only, as the invention may be modified and practiced in different but equivalent manners apparent to those skilled in the art having the benefit of the teachings herein. For example, the process steps set forth above may be performed in a different order. Furthermore, no limitations are intended to the details of construction or design herein shown, other than as described in the claims below. It is therefore evident that the particular embodiments disclosed above may be altered or modified and all such variations are considered within the scope and spirit of the invention. Accordingly, the protection sought herein is as set forth in the claims below.