EP0044295A1 - Systeme ferme a pompe de chaleur produisant de l'energie electrique - Google Patents

Systeme ferme a pompe de chaleur produisant de l'energie electrique

Info

Publication number
EP0044295A1
EP0044295A1 EP80900898A EP80900898A EP0044295A1 EP 0044295 A1 EP0044295 A1 EP 0044295A1 EP 80900898 A EP80900898 A EP 80900898A EP 80900898 A EP80900898 A EP 80900898A EP 0044295 A1 EP0044295 A1 EP 0044295A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
fluid
condenser
heat pump
pump system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP80900898A
Other languages
German (de)
English (en)
Inventor
Gerald F. Humiston
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0044295A1 publication Critical patent/EP0044295A1/fr
Withdrawn legal-status Critical Current

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
    • F01K25/08—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 special vapours
    • F01K25/10—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 special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F01K25/106—Ammonia
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
    • F03G7/05—Ocean thermal energy conversion, i.e. OTEC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24V—COLLECTION, PRODUCTION OR USE OF HEAT NOT OTHERWISE PROVIDED FOR
    • F24V50/00—Use of heat from natural sources, e.g. from the sea
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2254/00—Heat inputs
    • F02G2254/30—Heat inputs using solar radiation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • This invention relates to a heat pump process and apparatus which is applicable to the generation of elec ⁇ trical power, production of mechanical power, and cooling of discharges from nuclear and thermal electrical generating plants and more particularly to a process and apparatus comprising an evaporator and a condenser where the heating necessary to cause evaporation in the evaporator and the cooling necessary to cause condensing in the condenser are obtained from warm and cold fluid sources.
  • the heat pump has been known as one of the most effici methods for heating and cooling with the application of small amounts of external energy.
  • Application of heat pump principles appear to offer the solutions for obtaining usable energy from the aforementioned energy sources with low specific energies.
  • heat pump systems have been designed to obtain the maximum amount of heat transfer from one source to another source with the minimum amount o power applied..
  • To utilize heat sources of low specific energy for the production of energy it is now necessary to devise heat pump systems that will produce the maximum amount of energy with the minimum amount of heat energy applied.
  • an object of the present invention to provide a process and an apparatus into which a prime mover is driven by the pressure difference between the evaporator section of the apparatus and the lower saturation pressure of the refrigerant in the condenser section of the apparatus.
  • a further object of the present invention is to provide a means of controlling the speed of the prime mover means regardless of variations in the load on the generator means, by means of a control valve means and conduit means in parallel with the prime mover means which is capable of by ⁇ passing a portion of the flow of refrigerant vapors from the evaporator means to the condenser means, thereby controlling the pressure across the prime mover means.
  • Yet another object of the present invention is to provide a heat exchanger means and a pump means to bring the refrigerant in the evaporator means into thermal contact with the warm fluid source, effectively replacing the heat of vaporization lost in the evaporator means by the evapora ⁇ ting of the refrigerant.
  • Still another object of the present invention is to provide a heat exchanger means within the condenser means wherein the refrigerant vapors in the condenser means are brought into thermal contact with the cooling fluid to remove the heat of condensation.
  • Another object of the present invention is to provide closed system in which a refrigerant is present at satura ⁇ tion pressures corresponding to the saturation pressures fo the given refrigerant at the various temperatures that are present in the system.
  • Another object of the present invention is to provide prime mover of the positive displacement type with the lowest possible volumetric efficiency in order to derive th maximum power from the existing and available pressure differentials while requiring the least mass flow of re ⁇ frigerant vapors and subsequently requiring the least energ from the fluid sources.
  • This process and apparatus comprises a closed heat pum system containing a refrigerant such as ammonia, freon,
  • OM water, carbon dioxide, carrene, or any other suitable refrigerant and comprises an evaporator means and a condenser means.
  • Conduit means connects the evaporator to the con ⁇ denser means.
  • Heat exchanger means and pump means brings the refrigerant in the evaporator means into thermal contact with the warm water source.
  • Heat exchanger means within the condenser means and a pump means brings the refrigerant vapors in the condenser means into thermal contact with the cold water source.
  • a pump means and conduit means returns the condensed refrigerant, liquid, back into the evaporator means.
  • a liquid level control means within the evaporator means and a divert valve means allows the refrigerant to flow from the condenser means to the evaporator means when the level of the refrigerant in the evaporator means when the level of the refrigerant in the evaporator is less than the desired level and allows the refrigerant to flow back into the condenser means when the refrigerant level in the evaporator means is satisfactory.
  • a prime mover means is interposed into the conduit means connecting the evaporator means to the condenser means.
  • An electrical generator means is coupled to the said prime mover means to convert all or part of the power developed in the prime mover means to electrical power.
  • An electrical control means is connected to the electrical generator means to direct the electrical power from the electrical generator means to the elements of the apparatus which require electrical power, and further, to direct excess electrical power for external usage.
  • a controllable valve means and conduit means is disposed in parallel with the prime mover means, whereby the refrigerant vapor flow can by-pass the prime mover means as a means to control the speed of the prime mover means compensating for variations in loads on the electrical generator means.
  • An optional enclosure may enclose the heat exchanger means with an inlet means and an outlet means and a recirculating pump means to provide increased heat exchanger efficiency due to the forced circulation of the warm water source through the enclosure.
  • a fundamental characteristic of the heat pump system comprises a closed loop system established between an evaporator means and a condenser means.
  • the heat to the evaporator means is furnished by the warm water source, and the cooling, or condensing, means in the condenser means is furnished by the cold water source, the process operating at the saturation pressures for the • refrigerant.
  • the prime mover means is interposed in the closed loop to provide mechanical power as well as power to drive an electrical generator means.
  • An electrical control means directs electrical power to the elements of the apparatus, and further directs excess electrical power for external usage.
  • a pump means, conduit means, divert valve means and a liquid level control means return the condensed refrigerant, liquid, to the evaporator means in a controlle manner.
  • the speed of the prime mover means is controlled b a controllable valve means and conduit means in parallel with the prime mover means.
  • the power developed by the said prime mover means is a function of the pressure differential across the prime move means.
  • the pressure differential is the difference between the saturation pressure of the refrigerant in the evaporato means, which is heated by the warm water source, and the saturation pressure of the refrigerant in the condenser means, which is cooled by the cold water source. Since the prime mover is of the positive displacement type, the amoun of refrigerant vapors passing through the prime mover means is a function of its volumetric efficiency. Therefore, it
  • 0 is desirable to use a positive displacement prime mover with the lowest possible volumetric efficiency in order to use the least amount of refrigerant vapors and therefore obtain the maximum amount of generated power for the amount of heat available.
  • Fig. 1 illustrates a specific example of the instant invention, namely an apparatus capable of the production of mechanical power and electrical power generation using only the energy available from low specific energy sources, namely two fluid sources at different energy potentials as a result of their differences in temperature.
  • FIG. 1 therein illustrated is one embodiment of an apparatus for the production of mechanical power and the production of electrical power, which functions
  • OMPI •- Vv ' II-O . as a heat pump deriving the energy needed to sustain its ow operation, and additionally, excess power for external usage, from two fluid sources at different energy levels as a result of their being at different temperatures.
  • a distinguishing feature of this invention is that the appa ⁇ ratus herein described and illustrated uses a positive displacement type of prime mover which derives its power from the pressure difference across the prime mover and being of low volumetric efficiency, displaces a minimum of refrigerant vapors. Since this is basically an adiabatic throttling process, extremely low temperature differences between the evaporator and condenser can be used to produce significant power as opposed to a turbine type of prime mover which would require large changes in enthalpy to obtain significant power.
  • the apparatus herein des ⁇ cribed and illustrated can use two fluid .sources at tempera ture differences, which have heretofore -been considered insignificant, to supply the energy necessary to power the apparatus.
  • the major components of the apparatus illustrated in Fig. 1 include an evaporator 12 which functions as a rese ⁇ rvoir for the refrigerant 13.
  • the pump 50 draws the refrigerant 13 from the evaporator 12 and by means of a conduit 5 pumps the refrigerant 12 into the heat exchanger 60 and the returns said refrigerant 13 to the evaporator 12 through a conduit 66, thereby bringing the refrigerant 13 into therma contact with the warm fluid source.
  • a condenser 30 contain therein a heat exchanger 32.
  • a pump 34 draws in fluid from the cold fluid source through a conduit 36 and pumps said fluid through the heat exchanger 32.
  • the cold fluid is subsequently returned to the cold fluid source by means of conduit 38.
  • a means has thus been established to bring the cold fluid from the cold fluid source into thermal contact
  • a conduit 14 connects the evaporator 12 and the condenser 30.
  • a prime mover 24 of the positive displacement type is interposed into the conduit 14.
  • An electrical generator 26 is coupled to the prime mover 24 to convert all or part of the power developed in the prime mover 24 into electrical power.
  • An electrical control 28 directs the electrical power produced by the electrical generator 26 to the elements of the apparatus which require electrical power, and further directs excess electrical energy for external usage.
  • a control means 16 senses the speed of the prime mover 24 and modulates the controllable valve 20.
  • a pump 42 draws condensed refrigerant vapors and liquid from the condenser 30 through a conduit 40 and pumps said refrigerant 13 through a conduit 44 to a divert valve 48.
  • a liquid level control 52 is located in the evaporator 12.
  • the liquid level control 52 maintains the desired level of refrigerant 13 in the evaporator 12 by controlling the divert valve 48, allowing the refrigerant 13 to flow into the evaporator 12 by means of conduit 54 when the level of the refrigerant 13 in the evaporator 12 is less than the desired level, and diverting the flow of said refrigerant 13 back into the condenser 30 when the level of the refrigerant 13 in the evaporator 12 is satisfactory by means of a conduit 46.
  • an enclosure 58 encloses the heat exchanger 60.
  • This enclosure is provided with an inlet means 62 and an outlet means 56. Flow of the warm fluid from the warm fluid source is induced by a recirculating pump 64.
  • a recirculating pump 64 Flow of the warm fluid from the warm fluid source is induced by a recirculating pump 64.
  • the warm and cold fluid sources are specifically the warm ocean surface water and the cold deep ocean water.
  • the closed apparatus 10 is initially evacuated of air and gas and charged with the refrigerant 13 to be used, let us say for the purposes of this example, ammonia.
  • the refrigerant 13 exists as a liquid to the level in the apparatus 10 to which it is filled and the balance of the apparatus 10 is then filled with the refrigerant 13 vapors at the saturation pressure for ammonia corresponding to the temperature of the appa ⁇ ratus 10.
  • the pressure in the apparatus 10 would be the saturation pres ⁇ sure of ammonia at 80°F, or 153 psia. Operation of the apparatus 10 is then instituted by means of auxiliary power equipment since no electrical power exists at the electrica control 28. Cooling or condensing water is then being pumped through the heat exchanger 32 within the condenser 3 by the pump 34 which draws in cold deep ocean water through conduit 36 and pumps the same to the heat exchanger 32. After passing through the heat exchanger 32, the cold or condensing water is returned to the ocean by means of conduit 38. Pump 50 draws refrigerant 13 from the evapora ⁇ tor 12 through conduit 54 and pumps the refrigerant 13 to the heat exchanger 60.
  • the refrigerant 13 returns to the evaporator 12 through conduit 66.
  • the recirculating pump 6 draws warm ocean surface water into the inlet 62 of the enclosure 58 and discharges this flow around the heat exchanger 60 and out of the outlet 56 of the enclosure 58.
  • the refrigerant 13 is thus effectively brought into thermal contact with a heating source, in this case warm surface ocean water.
  • the saturation pressure in the evaporator then becomes the saturation pressure of the refrigerant 13 corres- ponding to the temperature to which it is being heated by the warm ocean surface water and the saturation pressure in the condenser 30 is then the saturation pressure for the refrigerant 13 in the condenser 30, corresponding to the saturation pressure for the refrigerant 13 for the temp- erature to which the refrigerant is being cooled by the cooling, or deep ocean water.
  • the pressure in the evaporator 12 portion of the apparatus 10 would be 153 psia
  • the pressure in the condenser 30 portion of the apparatus 10 would be 107.6 psia, thus creating a pressure differential of 45.4 psi across the prime move 24.
  • the prime mover 24 is driven by this pressure differential and the mass flow of refrigerant vapors from the evaporator 12 to the condenser 30 would be a function of the volumetric displacement of the prime mover 24.
  • the electrical generator 26, driven by the prime mover 24, then provides the energy to operate the apparatus.
  • the condensed refrigerant vapors and liquid in the condenser 30 are returned to the evaporator 12 by means of pump 42, which draws the refrigerant 13 from the condenser 30 through conduit 40 and pumps this refrigerant 13 to the divert valve 48.
  • the liquid level control 52 controls the level of the refrigerant 13 in the evaporator by operating the divert valve 48, allowing refrigerant 13 to flow from the divert valve 48 to the evaporator 12 through conduit 54 when the level of the refrigerant 13 in the evaporator 12 is less than the desired level and diverting the refrigerant 13 flows back into the condenser 30 through conduit 46 when the level of the refrigerant 13 in the evaporator 12 is satisfactory.
  • the control 16 senses the speed of the prime mover 24 and controls the controllable valve 20 to maintain the speed of the prime mover 24 constant, compensating for variations in loads on the electrical generator 26.
  • a heat pump method of producing mechanical power and electrical power has thus been described, whereby the temperature differentials present in the ocean, or other warm and cold fluid sources, is the only energy required to power the said apparatus and provide excess power and/or electrical power for external usage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Biodiversity & Conservation Biology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Oceanography (AREA)
  • Sustainable Development (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Procede de production d'energie electrique ou la source d'energie pour un moteur a cycle Rankine est constituee par l'energie existante entre deux sources de fluide tel que l'eau chaude de la surface d'un ocean et l'eau froide des profondeurs d'un ocean. On fait circuler un refrigerant tel que de l'ammoniac entre l'evaporateur (12) et l'echangeur de chaleur de l'eau en surface (60). Le refrigerant est refroidi par circulation entre le condenseur (30) et l'echangeur de chaleur d'eau profonde (32). Un moteur a deplacement positif (24) est entraine par les gaz chauds qui sont ensuite condenses et recircules vers l'evaporateur. Une commande electrique (28) distribue la puissance au systeme et les charges externes. Une commande (16) regle la vitesse. Cet appareil resout le probleme de l'entrainement d'un evaporateur et d'un condenseur avec deux sources qui ont des temperatures relativement voisines.
EP80900898A 1980-01-28 1980-01-28 Systeme ferme a pompe de chaleur produisant de l'energie electrique Withdrawn EP0044295A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1980/000078 WO1981002229A1 (fr) 1980-01-28 1980-01-28 Systeme ferme a pompe de chaleur produisant de l'energie electrique

Publications (1)

Publication Number Publication Date
EP0044295A1 true EP0044295A1 (fr) 1982-01-27

Family

ID=22154174

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80900898A Withdrawn EP0044295A1 (fr) 1980-01-28 1980-01-28 Systeme ferme a pompe de chaleur produisant de l'energie electrique

Country Status (2)

Country Link
EP (1) EP0044295A1 (fr)
WO (1) WO1981002229A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101251092A (zh) * 2008-04-09 2008-08-27 甘玉祥 海水温差发电工作介质二次加热和同质冷却的方法及装置
FR2999228A1 (fr) 2012-12-07 2014-06-13 IFP Energies Nouvelles Procede et systeme de conversion d'une energie thermique en energie mecanique, notamment pour la conversion de l'energie thermique des mers

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3312054A (en) * 1966-09-27 1967-04-04 James H Anderson Sea water power plant
SE394741B (sv) * 1974-04-18 1977-07-04 Projectus Ind Produkter Ab Vermepumpsystem
FR2304771A1 (fr) * 1975-03-21 1976-10-15 Chaudronnerie Entr Indle Procede et appareillage de transformation de chaleur a relativement faible temperature en force motrice ou en energie
US3967449A (en) * 1975-05-29 1976-07-06 Beck Earl J Ocean thermal gradient power plant
US4030301A (en) * 1976-06-24 1977-06-21 Sea Solar Power, Inc. Pump starting system for sea thermal power plant
US4186311A (en) * 1977-06-17 1980-01-29 Humiston Gerald F Heat pump method of concentrating fluids
US4200807A (en) * 1977-09-15 1980-04-29 Humiston Gerald F Method of electrical closed heat pump system for producing electrical power

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8102229A1 *

Also Published As

Publication number Publication date
WO1981002229A1 (fr) 1981-08-06

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