WO2006028444A1 - Moteur thermique basse temperature - Google Patents

Moteur thermique basse temperature Download PDF

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Publication number
WO2006028444A1
WO2006028444A1 PCT/US2004/028526 US2004028526W WO2006028444A1 WO 2006028444 A1 WO2006028444 A1 WO 2006028444A1 US 2004028526 W US2004028526 W US 2004028526W WO 2006028444 A1 WO2006028444 A1 WO 2006028444A1
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WO
WIPO (PCT)
Prior art keywords
fluid
prime mover
discharge
discharge fluid
heat
Prior art date
Application number
PCT/US2004/028526
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English (en)
Inventor
Theodore Charles Saranchuk
Donald Edward Marksberry
Original Assignee
Terran Technologies, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Terran Technologies, Inc. filed Critical Terran Technologies, Inc.
Priority to PCT/US2004/028526 priority Critical patent/WO2006028444A1/fr
Publication of WO2006028444A1 publication Critical patent/WO2006028444A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/06—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using mixtures of different fluids

Definitions

  • Heat engines using air, steam, mixtures of air and steam, and other working media have been used for over a century, and most of these use a single gaseous fluid as a working medium.
  • the steam engine, especially the steam turbine has been the most popular and successful heat engine, and present commercial steam engines have maximum efficiencies of less than 40% in converting the energy available from fuel into shaft work.
  • Steam engines and other workable heat engines have used an external heat sink, either by direct discharge to the environment in an open cycle or to a condenser for a closed steam cycle system. It is not necessary to use a condenser to reject this latent heat to the environment. Under certain conditions, the latent heat of the prime mover can be transferred to a different portion of the system.
  • the range of operation is, however, extremely narrow and operation outside the range in either over-loaded or insufficiently loaded conditions will cause the unit to shut down. In this mode of operation, all the available heat energy is transferred to the mechanical work portion of the process.
  • the process of this invention enables the system to produce useable shaft work at ambient and lower temperatures provided the heat content of the heat source is high enough for that fluid.
  • This heat exchanger transfers remaining energy above the temperature of the fluid at the pressure in the storage unit.
  • Heat exchanger is also referred to as an accumulator because it both condenses and stores the working fluid. These steps can be performed by two components, but it is more practical to combine them.
  • the back pressure in the accumulator is maintained such that the temperature of the stored working fluid is significantly below the boiling temperature of the working fluid, e.g. R-134A.
  • This cold liquid is expanded through a flow restricting device to a significantly lower pressure state where it is expanded isobarically and absorbs the latent heat remaining in the saturated turbine discharge vapor.
  • the isobaric expansion occurs at 4 psia, which has an effective temperature of -60 degrees F.
  • This vapor absorbs the remaining latent heat of condensation in the discharge of the prime mover, resulting in a complete liquefaction of the discharge.
  • This can also be accomplished by expanding cold vapor as well as liquid.
  • expanding vapor is a less efficient method of removing the latent heat.
  • the direct removal of the vapor in the accumulator via the suction of a compressor that discharges into the prime mover header could keep the accumulator pressure at the desired level.
  • a method for producing power to drive a load using a working fluid circulating through a system that includes a turbine having an inlet and an accumulator containing discharge fluid exiting the turbine.
  • a high velocity stream of heated vaporized fluid is supplied at relatively high pressure to the turbine inlet and expanded through the turbine to a lower pressure discharge side of the turbine where discharge fluid exits the turbine.
  • the discharge fluid is vaporized by passing the discharge fluid through an expansion device across a pressure differential to a lower pressure than the pressure at the turbine discharge side. Latent heat of condensation is transferred from the discharge fluid being discharged from the turbine to the discharge fluid that has passed through the expansion device. Expanded discharge fluid, to which heat has been transferred from fluid discharged from the turbine, is returned, vaporized, to the turbine inlet.
  • the system includes a prime mover, such as a turbine, for driving a load, and having an inlet and discharge side, though which prime mover heated vaporized fluid at relatively high pressure is expanded to a lower pressure at the discharge side where discharge fluid exits.
  • An accumulator contains discharge fluid from the prime mover. Discharge fluid from the accumulator is vaporized by passing it through an expansion orifice across a pressure differential to a lower pressure than the pressure at the turbine discharge side.
  • a first heat exchanger transfers latent heat of condensation from discharge fluid being discharged from the turbine to the discharge fluid that has passed through the expansion device.
  • a boiler further heats and vaporizes discharge fluid to which heat has been transferred from fluid discharged from the turbine.
  • a compressor pumps vaporized fluid from the heat exchanger to the boiler, and a pump delivers liquid fluid from the accumulator to the boiler.
  • Figure 1 is a schematic diagram showing the components of a low temperature heat engine system according to this invention.
  • Figure 2 is a schematic diagram showing an alternate embodiment of the system of Figure 1 ;
  • Figure 3 is a schematic diagram showing an alternate embodiment of the system of Figures 1 and 2.
  • FIG. 1 illustrates a system that includes a heat exchanger 10, which functions as a boiler; a prime mover 12 such as turbine 12, which is the primary extractor of heat in the form of work; and a heat exchanger 14, which function as a cooler; and an accumulator 20, a storage vessel containing discharge fluid that has passed through the prime mover.
  • Compressor 16 draws suction from the condensate in accumulator 20 through line 26 and valve 22 to the inlet side of the compressor.
  • the condensate or discharge fluid flash boils at the heat exchanger 14 and extracts latent heat from the discharge fluid leaving turbine 12.
  • the expanded vapor is then scavenged by compressor 16, which maintains low pressure in accumulator 20, is compressed to a higher pressure, and is injected into a steam drum portion 34 of heat exchanger 10.
  • shaft couplings, belts and sheaves and other items that driveably connect the pump 18, compressor 16 and the load.
  • the load is an electric generator 17 driven by the turbine 12.
  • the power capacity of the system described with reference to Figure 1 is about fifteen horsepower.
  • the working fluid is Refrigerant 134-a, although other . fluids can be used.
  • the calculations and equations of state follow the process description. Pressure, temperature and enthalpy references are from Du Pont Suva 134-a thermodynamic properties tables.
  • the low-pressure side of the turbine 12 is first decreased to 14 psia by driving compressor 16 from an external source, such as a motor.
  • Feed pump 18, a positive displacement pump, may also be used or substituted for the compressor 16 in reducing the turbine outlet pressure to 14 psia. Because the pressure is at 14 psia, the liquid in the accumulator 20 is maintained at a temperature of -17 0 F by flash evaporation.
  • a valve 22, directly connecting accumulator 20 through fluid line 26 to the compressor 16 inlet, is closed.
  • a valve 24, connecting the compressor 16 to heat exchanger 14 and expansion device 28, is opened.
  • the compressor 16 expands liquid discharge fluid drawn from accumulator 20 through expansion device 28, preferably an orifice, and in order to vaporize the discharge fluid in heat exchanger 14 at a pressure of 4 psia. Heat from discharge fluid exiting the turbine is transferred in heat exchanger 14 to vaporized fluid that has passed through expansion device 28. The vaporized fluid that has passed through expansion device 28 is at a temperature of -60 0 F.
  • the compressor 16 pumps vaporized discharge fluid into the steam drum 34 of the boiler 10.
  • Heat from an external heat source is transferred at heat exchanger 10 to the working fluid.
  • This heat can be from any source compatible with the fluid being used, such as process cooling water or ambient air.
  • air at +45 0 F is used.
  • Fans or blowers 30 force air through a tube fm heat exchanger 10 configured as a boiler, which includes a boiling tank 32 and a steam drum 34.
  • Vapor exiting boiler 10 is expanded in a convergent/divergent nozzle 35 such that the pressure differential between the boiler side and the back pressure side of the prime move 12 is converted into velocity.
  • the prime mover may be an impulse turbine.
  • a bladeless disk turbine 12 is preferred because of the significantly greater resistance to destruction that disk turbines provide under the conditions of this system compared to bladed turbines.
  • a bladeless disk turbine is also known as a Tesla turbine.
  • Disk pumps are capable of pumping boiling water, and disk turbines are not destroyed by condensate passing through the boundary layers of the disks.
  • Disk turbines the power range of this system can also be obtained at significantly lower cost than either piston engines or bladed turbines, and they can be very efficient in the range up to 100 kilowatts.
  • Alternative prime movers include a blade turbine, a centrifugal turbine, a vane motor, and a piston motor.
  • the disk turbine 12 has approximately a six inch diameter and the rotational speed is 7200 rpm to allow the speed to be stepped down by a speed reducer 37 to 3600 rpm, or 60 Hz to drive the generator 17.
  • the nozzle diameter is approximately 0.25 inch diameter. The determinations of nozzle size, disk spacing, disk thickness and number of disks is included with the calculations to demonstrate a preferred design.
  • the turbine produces power to drive the generator load 17, which is driveably connected through a 2: 1 speed reducer 37 to the turbine shaft.
  • the compressor 16, fan/blower 30, and feed pump 18 can be mechanically driven from the turbine shaft or from the electrical output of the generator 17. Horsepower requirements for these components are given in the calculations that follow.
  • the condensed fluid and any remaining vapor at 14 psia, the back pressure of the turbine, is at -17 (-16.8)°F as the discharge fluid exits the turbine and flows to accumulator 20.
  • the discharge fluid exiting the turbine 12 transfers its latent heat in heat exchanger 14 to the -6O 0 F vaporized fluid that has passed through expansion device 28 and flows to the compressor inlet or suction intake 46.
  • this heat exchange completely liquefies the turbine discharge fluid using the Von Linde process.
  • heat exchanger 14 is a counter-flow heat exchanger, located in accumulator 20 with the discharge fluid from turbine 12.
  • the process requires a load to function properly. When no load is present, a high back pressure results, and reduced output or no output is produced.
  • Vaporized discharge fluid can be removed by compressor 16 directly from the accumulator 20 without passing through expansion device 28 or heat exchanger 14.
  • the compressor 16 draws vaporized discharge fluid from accumulator 20 and pressurizes the vaporized discharge fluid slightly above the pressure in the vapor drum 34, to which it is delivered through valve 55.
  • vaporized discharge fluid pumped by compressor 16 from accumulator 20 can be passed through valves 52, 54 and heat exchanger 50, where heat from the compressed discharge fluid is transferred to an external media after leaving the compressor 16 en route to the vapor drum 34.
  • Heat exchanger 50 extracts latent heat from at least a portion of the compressor discharge fluid and transfers that heat to another fluid that flows through heat exchanger 50 to a heat sink, or to provide a heat source for a building or for another purpose.
  • Discharge fluid leaving compressor 16 is either delivered to vapor drum 34, from which it is returned to the turbine inlet, or it is returned to accumulator 20, as described with reference to Figure 3.
  • FIG. 1 shows that liquid discharge fluid from accumulator 20 is pumped through lines 38, 40 by a positive displacement pump 18 to a boiler liquid drum 32, where it is heated upon passing through heat exchanger 10.
  • the liquid discharge fluid is vaporized by heat transferred in the heat exchanger 10 from a media such as air or another external fluid.
  • FIG. 2 shows that liquid discharge fluid from pump 18 may travel an alternate path through valve 58 and an expansion device 62, which is preferably an orifice, to a heat exchanger 56. Temperature of the liquid discharge fluid is reduced upon expansion through orifice 62, and the discharge fluid is heated in heat exchanger 56 where it extracts heat from an external heat source, such as fluid from a process or the environment. Heated discharge fluid leaving heat exchanger 56 passes through valve 60 en route to the vapor drum 34. Heat exchangers 50, 56 allow heat input to, and/or heat output from the system directly from the working fluid in addition to the normal output of the prime mover 12.
  • FIG. 3 shows that liquid discharge fluid exiting heat exchanger 50 may be returned through valve 70 to accumulator 20 instead of, or in addition to flowing to vapor drum 34.
  • vaporized discharge fluid exiting heat exchanger 56 may be returned through valve 72 to accumulator 20 instead of, or in addition to flowing to vapor drum 34.
  • the various fluid flow paths are opened and closed using additional flow control valve 68; the system components are protected from over pressurization using pressure relief valves 74, 76; vent valves 78, 80 and fill valves 42, 82 allow charging and discharging the working fluid during startup or maintenance; and process pressure is monitored by pressure gauge 84, which is opened to accumulator 20 through valve 86.
  • BTUH 1.085 X SCFM X ⁇ T(dry bulb) (air to fluid Hx)
  • BTUH 488 X GPM X ⁇ T(water) (water to fluid Hx)
  • State 1 is the liquid content of accumulator 20. It was chosen to be at 14 psia. because the temperature for bulk boiling of R134-a at 14 psia. is -17°F. This demonstrates the ability to set the internal conditions at or below temperatures encountered from Fall to Spring. This is also the state at the inlet to the feed pump 18.
  • State 2 is the high pressure feed pump 18 outlet condition. These are determined by the pressure of Rl 34a at the ambient conditions. These are 45° F for the boiler pressure and -17° F for the temperature conditions.
  • Il State 3 is the boiler/heat exchanger 10 outlet condition. These are determined by the pressure of Rl 34a at the external ambient (heat exchanger inlet) conditions. These are set at 45° F for the demonstration projects. This is also the turbine nozzle inlet state. At other ambient temperatures, a throttling valve or other flow/pressure regulating device can be used to obtain the desired mass flow rate.
  • State 4 is the turbine nozzle discharge condition. Pressure is converted into velocity in the convergent/divergent nozzle and the pressure is the same as the back pressure of the turbine (14 psia) and the temperature is still at 45° F.
  • State 5 is the condition at the turbine 12 discharge into the accumulator 20- reverse flow heat exchanger 14. Both 100% and 80% liquefaction of the fluid are presented and addressed.
  • State 6 is the conditions on the compressor suction side of the turbine discharge/accumulator inlet heat exchanger.
  • the mass flow requirement is determined by the power output desired.
  • the power is 15 shaft horsepower. Flows are derived from the need to produce this power with a 45° F energy source.
  • Hp (pump) specific gravity X head X flow / 3960 X pump efficiency.
  • ⁇ P 40 psi (accumulator to boiler)
  • X 2.3067 92.1ft (head)
  • Total Sensible BTUH - Air side is:
  • 1 Hp can deliver 2000 scfm with a drop of less than 6" static head (water column) across their heat exchangers.
  • quality 20 at turbine out (80% liquefaction), again with a single stage impulse turbine:
  • Liquid return (vf) 261,854 lb/min / 85.98 lb/cu-ft
  • Radii for disk turbomachinery is commonly determined from Hasinger and Kehrt's spacing determination:
  • A q ⁇ /v ⁇ 2
  • A q ⁇ /v ⁇ 2
  • the flow rate from above is 7.9 scfrn (at 85% efficiency) to produce 15 Hp.
  • v k 1.59261E-06 f ⁇ -sec.
  • the inlet (outer) radius is about 6 inches.
  • a minimum inner/outer disk radius ratio of 2.5 is too low. Use a ratio of 3.0 to increase the flow path and to increase the amount of condensate.
  • turbine design information is included for completeness.
  • Other prime movers could be used, including, but not limited to bladed turbines and piston engines.
  • edge velocity is 376.8 ft/sec.
  • the jet velocity needs to be twice this or 753.6 ft/sec. ( ⁇ .8 Mach)
  • the radius would be 0.50 in.
  • K 0.82.
  • the orifice plate is between .3 and .45 inches thick.
  • the flow rate is can also be controlled by an expansion valve, venturi, or throttling valve.
  • an expansion valve is used for fine control.
  • the compressor 16 discharges into the boiler steam drum segment 34, the upper manifold of the tube fin heat exchanger. The decreased pump and fan flow requirements have been ignored.
  • the power to raise a gas pressure from 1 atmosphere to 125 psi is approximately 28% of the compressor flow capacity.
  • 250 is for direct conversion of power plant steam or a thermal connection to an automobile or truck radiator.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une méthode de production de puissance pour entraîner une charge (17) au moyen d'un fluide de travail circulant dans un système comprenant un moteur premier (12) présentant une entrée et un accumulateur (20) contenant un fluide d'évacuation sortant du moteur premier. Le fluide d'évacuation est vaporisé lors de son passage dans le dispositif de dilatation (28) dans un différentiel de pression à une pression inférieure à la pression du côté d'évacuation du moteur premier. Une chaleur latente de condensation du fluide d'évacuation sortant du moteur premier est transférée par un échangeur de chaleur (14) pour évacuer le fluide circulant dans le dispositif de dilatation (28). Le fluide d'évacuation vaporisé peut être directement retiré de l'accumulateur (20) par un compresseur (16) dans lequel il est pressurisé légèrement au-dessus de la pression du tambour de vapeur (34), auquel il est directement distribué.
PCT/US2004/028526 2004-09-02 2004-09-02 Moteur thermique basse temperature WO2006028444A1 (fr)

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008022406A1 (fr) * 2006-08-25 2008-02-28 Commonwealth Scientific And Industrial Research Organisation Système de moteur thermique
WO2008022407A1 (fr) * 2006-08-25 2008-02-28 Commonwealth Scientific And Industrial Research Organisation Système et procédé pour produire du travail
WO2012151055A3 (fr) * 2011-05-02 2013-01-03 Harris Corporation Cycle combiné imbriqué hybride
WO2013176972A1 (fr) * 2012-05-22 2013-11-28 Harris Corporation Procédé et système pour produire un travail à partir d'un cycle thermique hybride avec chaudière basse pression
WO2013043999A3 (fr) * 2011-09-22 2013-11-28 Harris Corporation Cycle thermique hybride comprenant réfrigération incorporée
WO2014004597A1 (fr) * 2012-06-26 2014-01-03 Harris Corporation Cycle thermique hybride avec boucle de réfrigération indépendante
WO2014018654A1 (fr) * 2012-07-24 2014-01-30 Harris Corporation Cycle thermique hybride ayant une efficacité accrue
WO2014154869A1 (fr) * 2013-03-29 2014-10-02 Thiessard Jean Machine thermique cryogenique
GB2528830A (en) * 2014-05-29 2016-02-10 John Montgomery An application of a convergent and/or convergent-divergent nozzle for increasing the pressure of a working fluid
US9297387B2 (en) 2013-04-09 2016-03-29 Harris Corporation System and method of controlling wrapping flow in a fluid working apparatus
US9303533B2 (en) 2013-12-23 2016-04-05 Harris Corporation Mixing assembly and method for combining at least two working fluids
US9303514B2 (en) 2013-04-09 2016-04-05 Harris Corporation System and method of utilizing a housing to control wrapping flow in a fluid working apparatus
US9574563B2 (en) 2013-04-09 2017-02-21 Harris Corporation System and method of wrapping flow in a fluid working apparatus
EP4194693A1 (fr) * 2021-12-10 2023-06-14 Nalin Walpita Système de conversion d'énergie

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US4449368A (en) * 1983-05-02 1984-05-22 Chicago Bridge & Iron Company Apparatus and methods of cooling and condensing exhaust steam from a power plant
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US5507145A (en) * 1991-11-21 1996-04-16 Siemens Aktiengesellschaft Steam generating power station, process for operating the same, and interlinking network and process for its operation
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US6233938B1 (en) * 1998-07-14 2001-05-22 Helios Energy Technologies, Inc. Rankine cycle and working fluid therefor
US6347520B1 (en) * 2001-02-06 2002-02-19 General Electric Company Method for Kalina combined cycle power plant with district heating capability
US20020162330A1 (en) * 2001-03-01 2002-11-07 Youji Shimizu Power generating system
US20040050048A1 (en) * 2002-09-12 2004-03-18 Kalina Alexander I. Geothermal system
US6769256B1 (en) * 2003-02-03 2004-08-03 Kalex, Inc. Power cycle and system for utilizing moderate and low temperature heat sources

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US3636706A (en) * 1969-09-10 1972-01-25 Kinetics Corp Heat-to-power conversion method and apparatus
US4291538A (en) * 1980-01-04 1981-09-29 Chicago Bridge & Iron Company Power producing dry cooling apparatus and method
US4506508A (en) * 1983-03-25 1985-03-26 Chicago Bridge & Iron Company Apparatus and method for condensing steam
US4449368A (en) * 1983-05-02 1984-05-22 Chicago Bridge & Iron Company Apparatus and methods of cooling and condensing exhaust steam from a power plant
JPH0544405A (ja) * 1991-08-20 1993-02-23 Mitsubishi Heavy Ind Ltd 蒸気タービンプラント
US5699666A (en) * 1991-11-21 1997-12-23 Siemens Aktiengesellschaft Steam generating power station, process for operating the same, and interlinking network and process for its operation.
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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008022407A1 (fr) * 2006-08-25 2008-02-28 Commonwealth Scientific And Industrial Research Organisation Système et procédé pour produire du travail
EA014465B1 (ru) * 2006-08-25 2010-12-30 Коммонвелт Сайентифик Энд Индастриал Рисерч Организейшн Система теплового двигателя
WO2008022406A1 (fr) * 2006-08-25 2008-02-28 Commonwealth Scientific And Industrial Research Organisation Système de moteur thermique
US8991181B2 (en) 2011-05-02 2015-03-31 Harris Corporation Hybrid imbedded combined cycle
WO2012151055A3 (fr) * 2011-05-02 2013-01-03 Harris Corporation Cycle combiné imbriqué hybride
WO2013043999A3 (fr) * 2011-09-22 2013-11-28 Harris Corporation Cycle thermique hybride comprenant réfrigération incorporée
WO2013176972A1 (fr) * 2012-05-22 2013-11-28 Harris Corporation Procédé et système pour produire un travail à partir d'un cycle thermique hybride avec chaudière basse pression
WO2014004597A1 (fr) * 2012-06-26 2014-01-03 Harris Corporation Cycle thermique hybride avec boucle de réfrigération indépendante
US9038389B2 (en) 2012-06-26 2015-05-26 Harris Corporation Hybrid thermal cycle with independent refrigeration loop
WO2014018654A1 (fr) * 2012-07-24 2014-01-30 Harris Corporation Cycle thermique hybride ayant une efficacité accrue
WO2014154869A1 (fr) * 2013-03-29 2014-10-02 Thiessard Jean Machine thermique cryogenique
FR3003897A1 (fr) * 2013-03-29 2014-10-03 Jean Thiessard Machine thermique cryogenique
US9297387B2 (en) 2013-04-09 2016-03-29 Harris Corporation System and method of controlling wrapping flow in a fluid working apparatus
US9303514B2 (en) 2013-04-09 2016-04-05 Harris Corporation System and method of utilizing a housing to control wrapping flow in a fluid working apparatus
US9574563B2 (en) 2013-04-09 2017-02-21 Harris Corporation System and method of wrapping flow in a fluid working apparatus
US9303533B2 (en) 2013-12-23 2016-04-05 Harris Corporation Mixing assembly and method for combining at least two working fluids
GB2528830A (en) * 2014-05-29 2016-02-10 John Montgomery An application of a convergent and/or convergent-divergent nozzle for increasing the pressure of a working fluid
EP4194693A1 (fr) * 2021-12-10 2023-06-14 Nalin Walpita Système de conversion d'énergie

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