BINARY VAPOR CYCLE METHOD OF POWER GENERATION

Abstract: Binary vapor cycle method of electrical power generation wherein two refrigerant fluids can be used to operate an apparatus for generating mechanical and electrical power, in which the first condenser (18) serves as a heat source for the second evaporator (36). A vacuum is drawn on conduit (16) by pump (22) so that warm surface ocean water will evaporate to feed the first condenser (18), which is cooled by a refrigerant such as ammonia, the working fluid in the second heat pump. The evaporated ammonia, in turn, drives positive displacement pump (72) and is cooled by deep ocean water from pump (64). This apparatus solves the problem of operating a heat pump system with two sources that are relatively close in temperature.

Description: Description Binary Vapor Cycle Method of Power Generation Technical Field This invention relates to a binary vapor cycle method of electrical power generation and production of mechanical power which is applicable to the utilization of low specific energy sources, such as two water sources which exist in close proximity to each other, but at different tempera¬ tures. Background Art As the world's sources of fossilized fuels are rapidly depleting, alternate sources of power now under strict scrutiny include the so-called natural energies, such as solar power, indirect solar power, geo-ther al power, etc. One of the many faceted solutions to the development of new sources of energy appears to lie in the utilization of the energy differentials existing between two fluid sources at different temperatures, such as are present in tropical ocean waters, wherein the warm surface waters, which are solar heated, are at temperatures considerably higher than the cold deep ocean waters. Although the total energy existing in two large fluid sources at different temperatures is enormous, the energy existing per unit of weight or mass is very small. Accord- ingly, new and novel techniques and cycles are required to utilize the small amount of specific energy available to do productive work. The heat pump has been known as one of the most effi¬ cient methods for heating and cooling with a small amount of external energy. Application of heat pump principles appear to offer the solution for obtaining usable energy from the aforementioned low specific energy sources. Previously, heat pump systems have been designed to obtain the maximum amount of heat transfer from one source to another source with the minimum amount of 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. Therefore it is an object of this invention ,to provide a process and an apparatus which overcomes the aforementione inadequacies of the prior art devices and provides an improvement which is a significant contribution to the advancement of the heat pump art. Accordingly, it is an object of the present invention to provide a novel and improved heat pump system which is operable to produce mechanical power and/or electrical power using a warm fluid source for supplying heat to offset the heat loss which occurs during vaporization of a fluid and a cold source to effect condensing of the fluid vapors. It is also an object of the present invention to provide a process and an apparatus whereby a first heat pump system derives heat energy from a warm water source and delivers said heat energy to the evaporator of a second heat pump system, the heat exchanger means of the evaporator of the second heat pump system being the condensing means of the first heat pump system. It is also an object of the present invention to provide a process and an apparatus wherein the first heat pump system becomes the warm source, or energy source, for a second heat pump system wherein mechanical power and elec¬ trical power are produced. It is another object of the present invention to provide a process and an apparatus wherein the second heat pump into which a prime mover has been interposed which is driven by the pressure difference between an evaporator section of the apparatus, which contains a refrigerant and is at the saturation pressure of the refrigerant for the corresponding temperature of the refigerant, which is heated by the first heat pump, and the lower saturation pressure of the cooler refrigerant in the condenser section of the apparatus which is cooled by the cold fluid source, and the mass flow of refrigerant vapors between the evaporator and the condenser sections of the apparatus. It is a further object of the present invention to provide a means of converting all or part of the output of the said prime mover means to electrical energy by means of an electrical generator means and an electrical control means. It is still another object of the present invention to provide a controlled means within the second heat pump system, of returning the condensed refrigerant, liquid, from the condenser means to the evaporator means to replace the said refrigerant evaporated in the said evaporator means. A further object of the present invention is to provide a means within the second heat pump for controlling the speed of the prime mover means regardless of variations in the load on the generator means by means of a control valve and conduit in parallel with the prime mover which is capable of by-passing a portion of the flow of refrigerant vapors from the evaporator to the condenser thereby control- ling 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 of the second heat pump system into thermal contact with the water vapors in the condenser of the first heat pump system. The heat of condensation of the vapors in the condenser of the first heat pump in thermal contact with the said heat exchanger provides the means by which the heat of vaporization lost in the evaporator of the second heat pump is constantly being replaced. Still another object of the present invention is to provide a heat exchanger means within the condenser of the second heat pump system, wherein the refrigerant vapors of the second heat pump system within the condenser means are brought into thermal contact with the cooling or condensing water, thereby removing the heat of condensation, which is equal to the heat of vaporization. Another object of the present invention is to provide means of removing condensate water from the condenser of th first heat pump system by means of a barometric conduit, or alternatively, removing said condensate water by conven¬ tional pump and conduit means, or alternatively, returning the said condensate water to the water source by means of a barometric conduit. It is still another object of the present invention to provide, within the first heat pump system, a process and a apparatus which is capable of operating by a vacuum pump means at the temperature* of the warm water source, thereby eliminating the need for the addition or conventional energy. Another object of the present invention is to provide, within the second heat pump system, a prime mover of the positive displacement type with the lowest possible vol- umetric efficiency in order to derive the maximum power fro the existing and available pressure differentials while requiring the least possible mass flow of refrigerant vapor and subsequently requiring the least energy from the water or fluid sources. Other objects and a fuller understanding of this invention may be had by referring to the summary of the invention, the description and the claims, taken in con¬ junction with the accompanying drawings. Disclosure of the Invention It has now been found that the foregoing and related objects can be readily attained in the novel and improved heat pump process and apparatus, hereinafter described, for the- production of mechanical power and the generation of electrical power, using fluid sources of low specific energy, but at different temperatures, as the means of powering the said process and apparatus. Although these two fluid sources could be oil, natural gas, atmospheric air, waste streams, salt water, fresh water or any other two fluids in which energy differentials exist as a function of their different temperatures, we shall, for simplicity, refer to the two fluids as a warm water source and a cold water source. The ' subject method can be divided into two separate heat pump systems, each performing a separate and distinct function. The first heat pump system is located between the warm water source and the second heat pump and uses the warm water source as the fluid of the heat pump system. The second heat pump system uses a conventional refrigerant such as ammonia, freon, carbon dioxide, carrene or any other suitable refrigerant, and uses the first heat pump as a warm source and the cold water source as a cooling or condensing source. The second heat pump is the heat pump process and apparatus that generates the power of the process. Thus this method, which is essentially a dual heat pump system, offers an approach to utilizing the advantages of two different refrigerants within a general apparatus. This is particularly advantageous in the utilization of low specific energy sources, such as two water sources which exist in close proximity to each other, but at different tempera¬ tures. Thus, water as a heat pump fluid can be used in a first heat pump to transmit heat energy to a second heat pump wherein the refrigerant is more suitable to the produc- tion of power by means of high saturation pressures at lower temperatures without incurring the disadvantages of water water vapors as a means to produce power. This is due to water's high specific volume and low saturation pressures low temperatures. Additionally, since the warm- water sources of energy most commonly available are in the form reservoirs, such as ocean waters, the utilization of baro¬ metric conduits to bring the warm water source into contac with the process eliminates the need for expensive heat exchangers which in the case of ocean water, are subject t fouling and loss of efficiency due to clinging microorganis First let us describe the first heat pump system whic can be used with the second heat pump system described herein or with any other heat pump system or in any other manner and with any other apparatus wherein it is advan- tageous to use the condenser means of the heat pump as a heat source for a further process. This heat pump system comprises an evaporating means, a condensing means and a warm water source. Conduit means connects the evaporator t the condenser. A barometric conduit connects the evaporato with the warm water source, such as warm surface ocean water, of such height as to form a barometric leg into whic the water will only rise to the desired height when the evaporator is at the negative pressure of the process. The condenser contains a heat exchanger which is connected to the second heat pump or such other process or apparatus int which the energy of this first heat pump system is to be pumped. A vacuum pump establishes the negative pressure of the apparatus, said negative pressure being the saturation pressure of the water of the warm water source at the temperature of the warm water source in the evaporator. A barometric conduit connects the condenser to the water source to return the condensed vapors or liquid in the condenser to the water source, or alternatively, when the condensed vapors from the condenser are desired to be eliminated, since they are essentially distilled or desali¬ nated water, a barometric conduit and a valve permits the removal of the condensed vapors or liquid from the negative pressure of the apparatus. This removal of condensed vapors or liquid from the condenser means can also be accomplished by a conventional pump and conduit. A circulating pump and conduit located in the barometric conduit connects the evaporator to the warm water source. The circulating pump draws warm water from the warm water source through one of the conduit means and discharges this flow through the other conduit means upwardly in the barometric conduit to induce and assist the thermal circulation in the barometric conduit. Thus, a heat pump system has been established comprising a closed apparatus with a warm water source and. a condensing means, a method of bringing the warm water of the warm water source into contact with the evaporator means, a method of removing condensed vapors or liquid from the apparatus and a means of initially establishing the negative or saturation pressure. A fundamental characteristic of this first heat pump system, of which this invention is a novel variation, comprises a closed loop system established between an evaporator, where warm water is subjected to the conditions for evaporation and the water vapors leave the water carrying with them the heat of vaporization and a condenser wherein the water vapors are condensed, thereby liberating the heat of condensation, which is equal to the heat of vaporization. In the case of this first heat pump of the subject invention, the heat to the evaporator is furnished by a warm water source and the cooling or condensing means for the condenser is a subsequent process or apparatus attempting to withdraw heat energy from the condenser. The process and apparatus operates at the saturation pressures dictated by the various temperatures in the apparatus. The condensed water vapors collected in the condenser may be returned to the water source or removed from the apparatus for external usage, since these condensed vapors or liquid are essentially distilled or desalinated water. A vacuum pump establishes the initial negative or saturation pressure of the apparatu and during operation removes any non-condensable vapors or gases. The second heat pump system of the instant invention comprises a closed heat pump system containing a refrigeran such as ammonia, freon, water, carbon dioxide, carrene or any other suitable refrigerant and consists of an evaporato and a condenser. Conduit means connects the evaporator to the condenser. Heat exchanger means and pump means brings the refrigerant in the evaporator into thermal contact with the condenser of the first heat pump. Heat exchanger means within the condenser and pump brings the refrigerant vapors in the condenser into thermal contact with the cold water source. A pump means and conduit means returns the con¬ densed refrigerant or liquid back into the evaporator. A liquid level control within the evaporator and a divert valve maintains the level of the said refrigerant in the evaporator by means of the liquid level control controlling the divert valve allowing the condensed refrigerant to flow from the condenser to the evaporator when the level of the refrigerant in the evaporator is less than the desired level, and diverting the flow of the condensed refrigerant back into the condenser when the refrigerant level in the evaporator is satisfactory. A prime mover means interposed into the conduit connects the evaporator to the condenser. An electrical generator *is coupled to the prime mover to convert all or part of the power developed in the prime mover to electrical power. An electrical control connected to the electrical generator directs the electrical power from the electrical generator to the elements of the appa¬ ratus which require electrical power and further directs excess electrical power for external usage. A controllable valve and conduit, in parallel with the prime mover, enables the refrigerant vapor flow and subsequent pressure to bypass the prime mover to control the speed of the prime mover, compensating for variations in loads on the electrical generator. A fundamental characteristic of the second heat pump system, of which this invention is a novel variation, com¬ prises a closed loop system established between an evapora- tor means where a refrigerant is subjected to the conditions for evaporation and the refrigerant vapors leave the liquid refrigerant, carrying with them the heat of vaporization, and a condenser means, wherein the refrigerant vapors are condensed, thereby liberating the heat, of condensation which is equal to the heat of vaporization. In the case of the subject invention, the heat to the evaporator is furnished by the first heat pump and the cooling or condensing means in the condenser- is furnished by the cold water source, the process operating at the saturation pressures for the refrigerant used, dictated by the various temperatures in the apparatus. The prime mover interposed into the closed loop provides mechanical power as well as power to drive an electrical generator. An electrical control directs elec¬ trical power to the elements of the apparatus and further directs excess electrical power for external usage. A pump, conduit, divert valve and liquid level control returns the condensed refrigerant or liquid to the evaporator in a controlled manner. The speed of the prime mover is con¬ trolled by a controllable valve and conduit in parallel with the prime mover. The power developed by the prime mover is a function of the pressure differential across the prime mover. The pressure differential is the difference between the satura¬ tion pressure of the refrigerant in the evaporator, which is heated by the first heat pump system, energy which is indirectly from the warm water source, and the saturation pressure of the refrigerant in the condenser, which is cooled by the cold water source. Since the prime mover is of the positive displacement type, the amount of refrigeran vapors passing through the prime mover is a function of its volumetric efficiency, and therefore, it is desirable to us a positive displacement prime mover with the lowest possibl volumetric efficiency in order to require the least flow of refrigerant vapors from the evaporator to the condenser and therefore obtain the maximum amount of generated power for the amount of heat available from the first heat pump syste and the cooling effects from the cold water source. The practice of the instant invention enables an apparatus capable of producing mechanical power and elec¬ trical power generation using water sources, or other fluid sources of low specific-.energy by means of a dual heat pump system, more accurately described as a Binary Vapor Cycle. This invention accordingly comprises a process and an apparatus possessing the features, properties and the relationship of elements which will be exemplified in the article hereinafter described, and the scope of the inven¬ tion will be indicated in the claims. Brief Description of the Drawings For a fuller understanding of the nature and objects o the invention, reference should be had to the following detailed description taken in connection with the accom¬ panying drawings in which: Fig. 1 is a diagram of a first heat pump system and a second heat pump system embodying the instant invention, with the means of returning the condensate water of the first heat pump system being a barometric conduit to the water source; -- Fig. 2 is a diagram of the first heat pump system wherein an alternate method of removing condensate water from the apparatus is illustrated; and Fig. 3 is a diagram of the first heat pump system wherein another alternate method of removing condensate water from the apparatus is illustrated. Similar reference characters refer to similar parts throughout the several views of the drawings. Best Mode for Carrying Out the Invention Referring now to Fig. 1, therein illustrated is one embodiment of an apparatus comprising two heat pump systems, in which the first heat pump system is the means by which the heat energy from a warm water source is used to apply the heat energy to a second heat pump means, which is the means of producing mechanical and electrical power suffi¬ cient to sustain the operation of the first and second heat pump systems and additionally to provide 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 apparatus herein described and illustrated uses two heat pump systems connected in series to form a binary vapor cycle system in which the warm water or warm fluid source is the heat pump fluid or refrigerant, and a conventional refrigerant is used in the second, or power producing, heat pump system. This second heat pump system contains 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 the 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. Thus, the apparatus herein described and illustrated can use two water or fluid source at temperature differences, which have heretofore been considered insignificant, to supply the energy necessary to power the apparatus, and additionally to supply excess energy for external usage. The major components of the first heat pump system of the apparatus 10 illustrated in Fig. 1 include an evaporato 14 connected to a condenser 18 by a conduit 16. A baro- metric conduit 12 connects the evaporator 14 to the warm water source. The barometric conduit 12 is of such height that the water from the warm water source will only rise to the desired level when the apparatus 10 is at the saturatio pressure, negative, of the water in the evaporator 14. A barometric conduit 24 connects the condenser 18 with the water source. The height of the barometric conduit 24 is sufficient to allow water from the water source to only ris to the desired height when the condenser 18 is at the saturation pressure, negative, of the water in the condense 18. A vacuum pump 22 establishes the initial saturation pressure in the apparatus 10 and thereafter removes non- condensable vapors and gases from the apparatus 10 during operation. A pump 28 draws in water from the warm water source through a conduit 26 and discharges this flow throug conduit 30 upwardly in the barometric conduit 12 to induce and assist thermal circulation of the warm water source in the barometric conduit 12. With further reference to Fig. 1, a specific example o the first heat pump system is illustrated wherein the warm water source is specifically the warm ocean surface water and the cooling or condensing means in the condenser is the heat exchanger coupled to the second heat pump system. The process is instituted initially by the vacuum pump 22 evacuating the air from the closed system. The vacuum pump -13- 22 reduces the pressure in the closed system until the pressure in the system reaches the saturation pressure dictated by the temperature of the warm ocean surface water. In the case of ocean surface water at 80°F, the pressure left in the apparatus 10 would be the saturation pressure of water at 80°F or approximately 0.507 psia. With the con¬ tinued operation of the vacuum pump 22, the closed system then fills with water vapor at the saturation temperature and pressure 80°F and 0.507 psia. Because of the difference in the pressure in the closed first heat pump system and the pressure of the atmospheric air surrounding the closed system, the ocean water in con¬ duits 12 and 24 rises until the ocean water in the conduits has created a head pressure at the ocean surface equal to the atmospheric pressure. In the case of atmospheric pressure at 14.7 psia, the difference in pressure between the inside of the closed system and the atmospheric pressure outside of the closed system would be approximately 14.193 psi and would therefore cause the ocean water in conduit 12 and conduit 24 to rise approximately 31.8 feet above the surface of the ocean. A heat exchanger 20, coupled to the second heat pump system, is the cooling or condensing means for the water vapors in the condenser 18. When water vapors in the condenser 18 come into thermal contact with the colder heat exchanger 20, they are condensed, thereby liberating the heat of condensation, said heat of condensation providing the heat means to the second heat pump system. The conden¬ sed vapors or liquid are returned to the ocean by means of the barometric conduit 24. As the water vapors are condensed in the condenser 18 there is a considerable reduction in volume as the vapors become liquid, thereby drawing additional vapors from the evaporator 14, establishing a flow of water vapors from the evaporator 14 to the condenser 18. Heat for ^UREA^x continued evaporation in the evaporator 14 is provided the thermal circulation of the warm surface ocean water in conduit 12. This thermal circulation is induced and assist by the pump 28, which draws warm ocean surface water throug conduit 26 and discharges this flow through conduit 30 upwardly in the barometric conduit 12, thus establishing a non-random thermal circulation. The heat of vaporization lost to the vapors evaporated in the evaporator 14 are thus constantly replaced. Since the vapors caused by evaporation in the evaporat 14 are pure water vapors and do not contain the salts or minerals present in the ocean water and since the evaporato 14 is separated from the condenser 18 by a vapor conduit 16 the condensate water obtained as a result of the condensati of the vapors in the condenser 18 is distilled or desalina¬ ted water. The heat exchanger 20, which is the heat source for the second heat pump system, is thus not exposed to scaling or clinging microorganisms as would be the case if the heat exchanger 20 were to be brought into direct contac with the ocean water. Again with reference to Fig. 1, a specific example of the second heat pump system is illustrated, wherein the warm, or energy source, is the first heat pump system and the cooling or condensing source is cold deep ocean water pumped from deep beneath the ocean surface. The major components of the second heat pump system of the apparatus 10 illustrated in Fig. 1, include an evaporator 36 which functions as a reservoir for the refrigerant 37. The pump 40 draws the refrigerant 37 from the evaporator 36 and by means of a conduit 38 pumps the refrigerant 37 into the hea exchanger 20 and returns the refrigerant 37 to the evapora¬ tor 36 through a conduit 32 thus bringing the refrigerant 3 into thermal contact with the condenser 18 of the first hea pump system. A condenser 70 contains therein a heat exchan ger 68. A pump 64 draws in cold or condensing water, in this case, deep ocean water, through a conduit 62 and pumps the deep cold ocean water through the heat exchanger 68. The cold or condensing water is subsequently returned to the ocean by means of a conduit 66. A means has thus been established to bring the cold deep ocean water into thermal 5 contact with the refrigerant vapors within the condenser 70. A conduit 34 connects the evaporator 36 and the condenser 70. A prime mover of the positive displacement type 72 is interposed into the conduit 34. An electrical generator 74 is coupled to the prime mover 72 to convert all or part of 10 the power developed in the prime mover 72 into electrical power. An electrical control 76 directs the electrical power produced by the electrical generator 74 to the elements of the apparatus which require electrical power and further directs excess electrical energy for external usage. Con- 15 duits 44 and 48 and a controllable valve 46, placed in parallel with the prime mover 72, controls the speed of the prime mover 72 to a constant value by the capability of by¬ passing the flow of refrigerant vapors around the prime mover 72, thus compensating for variations in loads on the 20 electrical generator 74. A control means 50 senses the speed of the prime mover 72 and modulates the controllable valve 46. A pump 56 draws condensed refrigerant vapors 37, liquid, from the condenser 70 through a conduit 60 and pumps the refrigerant 37 through a conduit 58 to a divert valve 25 52. A liquid level control 42 is located in the evaporator 36. The liquid level control 42 maintains the desired level of refrigerant 37 in the evaporator 36 by controlling the divert valve 51, allowing the refrigerant 37 to flow into the evaporator 36 by means of conduit 38 when the level of 30 the refrigerant 37 in the evaporator 36 is less than the desired level, and diverting the flow of the refrigerant 37 back into the condenser 70 when the level of the refrigerant 37 in the evaporator 36 is satisfactory by means of a conduit 54. -^JE-EX^ -16- The second heat pump system illustrated, wherein the hot, or energy source is the first heat pump means and the cold or condensing source is cold deep ocean water, func¬ tions as follows: The closed second heat pump system is initially evacuated of air and gas and charged with the refrigerant 37 to be used, let us say for the purposes of this example, ammonia. The refrigerant 37 exists as a liquid to the level in the system to which it is filled and the balance of the system is then filled with the vapors of the refrigerant 37 at the saturation pressure for ammonia corresponding to the temperature of the system. For exampl if the system was 80°F, the pressure in the system would be the saturation pressure of ammonia at 80°F, or 153 psia. Operation of the system is then instituted by means of auxiliary power equipment, since no electrical power exists at the electrical control 76. Cooling water, cold deep ocean water, is then pumped through the heat exchanger 68 within the condenser 70 by the pump 64 which draws in cold deep ocean water through conduit 62 and pumps the same to the heat exchanger 68. After passing through the heat exchanger 68, the condensing water is returned to the ocean by means of conduit 66. Pump 40 draws refrigerant 37 from the evaporator 36 and by means of conduit 38, pumps the refrigerant 37 to the heat exchanger 20 and subsequently th refrigerant 37 is returned to the evaporator 36 by means of conduit 32. Since the heat exchanger 20 is in the condense 18 of the first heat pump system, the refrigerant 37 is thu brought into effective thermal contact with a heating source, in this case, the condensing water vapors of the first heat pump system, which liberate the heat of con¬ densation of the vapors to the heat exchanger 20. The saturation pressure in the evaporator 36 then becomes the saturation pressure of the refrigerant 37 corresponding to the temperature to which it is being heated by the first heat pump system, and the saturation pressure in the con¬ denser 70 is then the saturation pressure for the refrigera 37 in the condenser 70, corresponding to the saturation pressure for the refrigerant 37 for the temperature to which the refrigerant is being cooled by the cooling, or deep ocean water. In this example, if the effective temperature in ' the evaporator 36 were to be 83°F, the pressure in the evaporator 36 portion of the system would be 161 psia, and if the effective temperature in the condenser 70 were to be 50°F, the pressure in the condenser 70 portion of the system would be 89.19 psia, thus creating a pressure differential of 71.81 psi across the prime mover 72. The prime mover 72 is driven by this pressure differential and the mass flow of refrigerant vapors from the evaporator 36 to the condenser 70 would be a function of the volumetric displacement of the prime mover 72. The electrical generator 74, driven by the prime mover 72, then provides the energy to operate the apparatus. The condensed refrigerant vapors, liquid, in the condenser 70 are returned to the evaporator 36 by means of pump 56, which draws the refrigerant 37 from the condenser 70 through conduit 60 and pumps this refrigerant 37 to the divert valve 52. The liquid level control 42 controls the level of the refrigerant 37 in the evaporator 36 by opera¬ ting the divert valve 52, allowing refrigerant 37 to flow from the divert valve 52 to the evaporator 36 through conduit 38 when the level of the refrigerant 37 in the evaporator 36 is less than the desired level and diverting the refrigerant 37 flow back into the condenser 70 through conduit 54 when the level of the refrigerant 37 in the evap¬ orator 36 is satisfactory. The control 50 senses the speed of the prime mover 72 and controls the controllable valve 46 to maintain the speed of the prime mover constant, compen¬ sating for variations in loads on the electrical generator 74. The apparatus 10 has thus been described, comprising a first heat pump and a second heat pump, each of which can be used in other apparatus and for other applications as their functions dictate, which together in series comprises -SUR£4 O a heat pump method of producing mechanical power and elec¬ trical power, whereby the temperature differentials of two fluid sources, such as exist in ocean waters, is the only energy required to power the said apparatus and provide excess power and/or electrical power for external usage. Now referring to Fig. 2 of the drawings, a method is illustrated whereby the condensate water in the first heat pump system, which is a result of the evaporation and condensing process and therefore distilled or desalinated water, can be removed from the system without being return to the water source by means of the barometric conduit 24 connected to the water source. A different barometric conduit 80 is connected to the condenser 18 and is of such height as water in this barometric conduit 80 will create head pressure equal to the difference between the atmos¬ pheric pressure and the pressure in the condenser 18, plus an additional head sufficient to give the desired head pressure at the condensate water, valve 84. A liquid level control 78 located at the top of the barometric conduit 80 controls the condensate water valve 84 which is connected the barometric conduit 80 by a conduit 82, and allows the condensate water valve 84 to discharge condensate water through conduit 86, while maintaining the desired head in barometric conduit 80. The means have thus been provided remove condensate water from the system while the system i under negative, or saturation pressure. Now referring to Fig. 3 of the drawings, an alternate method is illustrated whereby the condensate water in the first heat pump system, which is a result of the evaporati and condensing process and therefore distilled or desali¬ nated water, can be removed from the system without being returned to the water source by conventional pump and valv means. A liquid level control 88 is located in the bottom portion of the condenser 18 at the level at which it is -19- desirable to maintain the level of the condensate water in the condenser 18. A condensate water pump 94 is connected to the condenser 18 by means of a conduit 90 and the outlet of the condensate water pump 94 is connected to divert valve 98 by means of a conduit 96. A conduit 92 connects divert valve 98 with condenser 18 and another conduit 100 is connected to divert valve 98 to remove the condensate water from the system. Condensate water from the condenser 18 collects in the bottom of the condenser 18 until this condensate water reaches the liquid level control 88, at which time the liquid level control 88 then regulates the action of divert valve 98, letting condensate water out of the system sufficiently to maintain the condensate water level in the condenser 18.by alternately diverting the flow of condensate water out of the system through conduit 100 ; when the level of condensate water in the condenser 18 is above the desired level, and diverts the flow of condensate water in the condenser 18 through conduit 92 when the level of condensate water in -the condenser 18 is at or below the desired level. It can thus be seen that an alternate method of removing condensate water from the condenser 18, even though the system is at a pressure considerably lower than that of the atmospheric air outside of the closed system, has been described. A heat pump method of producing mechanical power and electrical power, using a binary vapor cycle has thus been described whereby the temperature differentials present in the ocean, or any other warm and cold fluid source, is the only energy required to power the said apparatus and provide excess power and/or electrical power for external usage. The foregoing process and apparatus has a substantial savings over that of the prior art in that no conventional energy sources are required to operate the apparatus and the URE σ apparatus utilizes energy sources of low potential, low temperature differences, to effectively obtain significant power production. The present disclosure includes that contained in the appended claims as well as that of the foregoing descrip¬ tion. Although this invention has been described in its preferred form with a certain degree of particularity, it i understood that the present disclosure of the preferred for has been made only by way of example and numerous changes i the details of construction and the combination and arrange ment of parts may be resorted to without departing from the spirit and scope of the invention.

Claims: Claims 1. A heat pump system for producing electrical power, comprising in combination: a first and a second heat pump for a first and a second fluid, respectively; said first heat pump comprising a first evaporator and a first condenser interconnected by a first conduit; said second heat pump comprising a second evap¬ orator and a second condenser interconnected by a second conduit; means for introducing warm first fluid into said first evaporator; a closed first heat exchanger disposed in said first condenser for absorbing heat from the condensing first fluid; condenser return conduit means connecting said second condenser to said second evaporator and extending through said closed first heat exchanger for heating the condensed second fluid prior to introduction into said second evaporator; a prime mover interposed in said second conduit for providing mechanical energy from the mass flow of vapor from said second evaporator to said second condenser; an electrical generator coupled to said prime mover to convert said mechanical energy into an electrical power output; and electrical control means connected to said elec¬ trical generator for directing the electrical power output thereof to operate the heat pump system and for directing any excess electrical power output for external usage. 2. A heat pump system as set forth in claim 1, wherein the first fluid has different physical properties than the second fluid. • B ' UR-E ^ 3. A heat pump system as set forth in claim 1, wherein said condenser return conduit means forms a closed second heat pump. 4. A heat pump system as set forth in claim 3, including a second condenser pump interposed in said con¬ denser return conduit means for pumping the condensed secon fluid through said first heat exchanger to said second evaporator. 5. A heat pump system as set forth in claim 4, including liquid level control means connected to said condenser return conduit means for maintaining a desired level of the second fluid in said second evaporator. 6. A heat pump system as set forth in claim 1, including a bypass conduit connected in parallel with said prime mover; and bypass control valve means interposed in said bypass conduit for controlling the flow of the second fluid around said prime mover for controlling the speed thereof. 7. A heat pump system as set forth in claim 1, wherein said first evaporator is connected by a first evaporator conduit to the warm first fluid; and said first evaporator conduit forming a barometri leg between the low internal pressure of said first evap¬ orator and the ambient. 8. A heat pump system as set forth in claim 1, including a first condenser conduit for forming a barometri conduit to return the condensed first fluid to the ambient. o:. 9. heat pump system as set forth in claim 1, including a first condenser pump interconnected to said first condenser for pumping the condensed first fluid from said first condenser. 10. A heat pump system as set forth in claim 9, including level control means connected to said first condenser pump for controlling the level of condensed first fluid in said first condenser. 11. A heat pump system as set forth in claim 1, including an evaporator return conduit for circulating the second fluid in said second evaporator through said closed first heat exchanger. '12. A heat pump system as set forth in claim 11, including a second evaporator pump interposed in said evaporator return conduit for circulating the second fluid through said closed first heat exchanger means back to said second evaporator. 13. A heat pump system as set forth in claim 1, including a closed second heat exchanger disposed in said second condenser for condensing the second fluid. 14. A heat pump system as set forth in claim 13, including a second heat exchanger pump for circulating a cool fluid through said second heat exchanger. _OM.FI

Inventors: HUMISTON G
Applicants: HUMISTON G
Application year: 1980
Main classification: H02P9
IPC codes: F01K25, F02G1, F03G7