Vapor force engine

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WAPOR FORCE ENGINE PSIA (234 kPa) and 450° C. at 51 PSIA (352 kPa. Although there are no efficiency figures Stated in this patent, the use of

This is a divisional of application(s) Ser. No. 08/852,631 Such high temperatures and low preSSures must have a filed on May 7, 1997, U.S. Pat. No. 5,946,916, which is a detrimental influence on the overall efficiency of the turbine. division of 08/277,524, filed on Jul. 19, 1994, abandoned. In U.S. Pat. No. 4,700,543 to Krieger et al., a plurality of

BACKGROUND OF THE INVENTION

independent, closed Rankine cycle power plants, each of which has a vaporizer and is operated by Serially applying a 1. Field of the Invention medium or low temperature Source fluid to the vaporizers of The invention relates in general to a vapor-driven piston the power plants for producing heat-depleted Source fluid. type engine and in particular to a vapor-driven piston-type The heat-depleted source fluid is applied to all of the engine that has a first fluid therein that receives heat from a preheaters in parallel. The power plants are shown to be heat Source to vaporize the fluid and drive the piston engine turbines.

and which includes therein a Second closed fluid path in heat Thus, there is a significant need in the art for a vapor eXchange relation with the first fluid path to increase the 15 driven piston-type engine that has high efficiency and which efficiency of the engine. In a still further embodiment, a operates at relatively low temperatures. plurality of the efficient vapor-driven piston-type engines are SUMMARY OF THE INVENTION coupled one to another in different closed circuits whereby the fluid in the first closed circuit in a Second or Subsequent The present invention aims to remedy these disadvantages Vapor-driven piston-type engine is heated by the first vapor and to provide a highly efficient vapor-force piston device driven piston-type engine or by the fluid flowing through it. whose operation is relatively inexpensive and which, in a 2. Description of Related Art particular embodiment, enables practical use to be made of A conventional vapor force piston device contains a temperature Sources at a relatively low temperature, thus Vaporizable fluid, an evaporator for vaporizing the fluid, the enabling the use of inexpensive fuels. Vapor piston machine and a closed circuit in which the 25 The results are achieved with the present invention evaporator and the vapor piston machine are interposed for because the fluid used in the machine is a fluid with an the transport of the fluid. Such a conventional vapor force atmospheric evaporation temperature lower than 50 C. and device of this Sort may be a Steam power plant which uses with Such evaporation characteristics that even at a low water as a fluid. The evaporator is the Steam generator and temperature, high pressure vapor is obtained. Suitable fluids the vapor machine is a Steam engine with pistons or a steam are, in particular, those fluids which are used in cooling turbine driving a current generator. installations Such as fluorohydrocarbons or an equivalent However, water evaporates at 100° C. under atmospheric alternative. A very well-suited fluid, therefore, is 1,1- pressure. In order to obtain a good efficiency, over-heated or dichloro 2.2.2-trifluoroethene.

Super-heated Steam at an even far higher temperature is According to a special embodiment of the invention, the required. This implies that for the evaporation in the Steam 35 evaporator is a heat eXchanger having the above-mentioned generator, high quality and quantities of fuel are required. It fluid as a Secondary fluid and another liquid as the primary further implies that the device cannot work on heat alone at fluid. The heat eXchanger may, in a practical Sense, form the a relatively low temperature even though it may be available radiator of an explosion engine, Such as an automobile in large amounts. Thus the Supplied energy is relatively engine, whose coolant forms the primary fluid. expensive. 40 Alternatively, the heat eXchanger may be a device that In U.S. Pat. No. 3,218,802 and issued in the name of D. eXchanges heat between a hot gas and a fluid or may be a R. Sawle, a binary vapor power plant includes a Sulfur cycle boiler that is filled with the primary fluid and that is heated consisting of a heat Source 10 which heats and vaporizes by a heat Source. The heat Source may be a burner, an electric Sulfur, a first stage Sulfur heat engine 12 which converts the resistor, Solar energy, and the like. heat in the vapor into kinetic energy, and a heat eXchanger 45 In another embodiment of the invention, the evaporator 14 that receives the partially cooled Sulfur and removes the itself contains the heat Source. This heat Source may be a remainder of the heat. The heat exchanger 14 heats the fluid burner, a reflective mirror in a Solar energy installation or an in conduits 37, 41, and 43 to convey Steam to a Second Stage electric resistor. It may also be an explosion engine, Such as heat engine 16. Similar Systems have been employed at an automobile engine, wherein the fluid Serves as a coolant petrochemical plants that use ethylene-oxide reactors. The 50 for the automobile engine. In case the heat is Supplied by reactors are cooled by a high temperature, low preSSure fluid Such automobile engine, the vapor machine can be con (diphyl fluid). This fluid is sent to a heat exchanger to nected to the power output shaft of the engine or may be produce the Super-heated Steam. The Steam was used in a formed in one and the same engine block with the explosion Steam turbine to compress ethylene gas. This System has engine and thus both the vapor machine and the explosion very difficult problems to overcome since using Sulfide, 55 engine are coupled to the Same power output shaft. Sulfur, phosphorus or even Sodium is excluded because Steel In accordance with another embodiment of the invention, is hydrogen permeable and hydrogen with the above mate the vapor force device contains more than one vapor rials will give Severe problems. This is a very high tempera machine which are erected one after the other in the form of ture device with saturated sulfur vapor at 682 C. (1260 F). a cascade. In Such case, the plurality of vapor machines may In U.S. Pat. No. 4,070,862 issued to Doerner et al., a 60 be coupled to each other in closed circuits whereby the fluid turbine in power station plants is provided with two different in the fluid circuit for the Second or Subsequent vapor fluids such as water and H. One of the problems is the machine is heated by the first or preceding vapor machine leakage from one turbine Site to the other. The invention is and/or by the fluid running through it. Again, in Such case, a choice of two liquids where the Second liquid has a lower the fluids in the Successor circuits may be different, Such as boiling point than the first liquid and returns the vapor 65 each having a different temperature function. condensate (linkage) to the boiler. The two liquids have low Thus, it is an object of the present invention to provide a pressures compared to their temperatures at 800° C. with 34 Vapor force engine that has a primary fluid therein that is

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heated by the waste heat from an explosion engine Such as Vapor greater than 10 bar is provided to the vapor input of an automobile engine that has a fluid circulating there the vapor driven piston-type engine. through to cool the explosion engine. The invention also relates to a low temperature vapor It is also an object of the present invention to provide an force engine comprising n vapor driven piston-type engines explosion engine and a vapor force engine within a common where ne2, each vapor-driven piston-type engine having a housing and both having pistons coupled to a common Vapor fluid inlet and a fluid outlet, a first heat eXchanger output drive Shaft, the explosion engine being cooled by a coupled to the vapor inlet and the outlet of a first one of the first fluid that is heated to a first temperature and the vapor Vapor-driven piston-type engines for receiving the fluid from force engine being driven by a Second fluid having a the fluid outlet of the first one of the vapor-driven piston Vaporizing characteristic that is at a lower temperature than type engines, a heat Source for Selectively coupling to the the first temperature of the cooling fluid of the explosion first heat eXchanger to vaporize the fluid therein at a tem engine and that is coupled in heat transfer relationship to the perature less than 180° C. (356°F) for powering the first one fluid of the explosion engine to be vaporized and drive the of the vapor-driven piston-type engines, a Second heat Vapor engine. eXchanger for receiving the fluid output from the first It is still another object of the present invention to provide 15 Vapor-driven piston-type engine at a temperature of less than a vapor engine and an explosion engine mounted in the same 120° C. (248 F.), the vapor fluid of the second vapor-driven housing and wherein the vapor engine has a first fluid therein piston-type engine being coupled to the Second heat that cools the explosion engine which vaporizes it to drive eXchanger for being vaporized at a temperature of less than the vapor engine. 120° C. (248 F.) to drive the second vapor-driven piston-type It is still another object of the present invention to mount engine, engine and each Succeeding vapor-driven piston-type having a heat eXchanger between it and the preceding a plurality of different vapor machines in the form of a cascade wherein the input fluid to the first vapor machine is Vapor-driven piston-type engine and having a vapor fluid of a temperature and character to drive the pistons therein therein that will vaporize and drive the Succeeding vapor and the waste temperature of the output fluid thereof is Such 25 driven piston-type engine at a temperature leSS than the as to heat a Second fluid in the Second engine to vaporize it temperature of the output fluid of the preceding vapor-driven and drive the Second vapor piston engine, the waste tem piston-type engine.

perature of the fluid output from the Second vapor engine BRIEF DESCRIPTION OF THE DRAWINGS being Such as to transfer heat to a third fluid in a third vapor These and other objects of the present invention will be piston engine to vaporize the third fluid and drive the third piston engine and then transmit the fluid output of the third more fully understood when taken in conjunction with the engine back to a heater to vaporize the fluid to begin the INGS following DETAILED DESCRIPTION OF THE DRAW cycle all over again. in which:

It is also an object of the present invention to cascade a accordingFIG. 1 represents a block diagram of a vapor force device plurality of different vapor machines Such that they are 35 to the invention;

mounted in Separate closed fluid circuits whereby a different FIG. 2 represents a block diagram analogous to that in fluid flows in each vapor machine and which receives its FIG. 1 but with reference to another embodiment of the input heat from the waste heat of the preceding vapor invention where the heat Source is an explosion-type engine machine. contained within the same housing as the vapor engine; It is an important object of the present invention to utilize 40 FIG. 3 is a block diagram analogous to that in FIGS. 1 and a vapor-driven piston-type engine that has a first fluid for 2 but with reference to yet another embodiment of the driving the pistons and a Second fluid circulating in a closed invention wherein the fluid that is vaporized and drives the loop within the engine in heat transfer relationship with the Vapor piston-type engine is the cooling fluid for the first fluid to thereby increase the efficiency of the vapor explosion-type engine that is housed in a common housing drive piston-type engine. 45 with the vapor-driven piston-type engine; Thus, the invention relates to a vapor force engine con FIG. 4 is a block diagram of another embodiment of the taining an vaporizable fluid, an evaporator for vaporizing present invention in which the fluid providing the heat Said fluid, a piston engine in a closed fluid circuit in which Sources for a plurality of cascaded vapor-type engines passes the fluid is vaporized, is coupled to the piston engine for through all of the cascaded engines, entering each engine at work, is condensed, and is returned to the evaporator, the 50 one temperature Sufficient to vaporize a fluid therein, exiting improvement comprising a vapor-driven piston-type engine the first engine at a temperature to vaporize the Second fluid having a vapor input and a fluid output, a heat eXchanger in the Second engine, exiting the Second engine at a still having an input and an output coupled to the engine, the heat lower temperature sufficient to vaporize a third fluid in the eXchanger receiving a low temperature fluid from the engine third vapor-type engine and coupling the fluid back to the fluid output and generating a vaporized fluid for the engine 55 heater for revaporizing the fluid and commencing the cycle Vapor input for driving the piston engine, an explosion OVer, engine cooled by a circulating fluid and Serving as a Source FIG. 5 is a block diagram of still another embodiment of of heat, a radiator on Said explosion engine for cooling the the invention in which each vapor machine has its own circulating fluid and forming the heat eXchanger Such that closed fluid circuit with the temperature of the output fluid the explosion engine circulating fluid is a primary fluid and 60 in one engine being Sufficient to vaporize a fluid in the the low temperature fluid for the vapor force engine is a Succeeding engine and all of which engines are coupled to secondary fluid that flows through the radiator in heat a common Shaft for providing an output;

eXchange relationship with and is vaporized by the heat of FIG. 6 is a Schematic diagram of a Baudino vapor-driven the primary fluid to drive the vapor piston engine, and the piston-type engine that has two closed fluid circuits and that low temperature Secondary fluid having an atmospheric 65 provides high efficiency;

evaporation temperature less than 240° C. (464 F) and FIGS. 7A and 7B are block diagram representations using having evaporation characteristics Such that high pressure a vapor force piston type engine Similar to that in FIG. 5

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S 6 except illustrating the details of each vapor engine and low temperatures, Such that the low-temperature heat Baudino motor all coupled to a common shaft; and Sources, which are abundantly available but cannot be easily FIGS. 8, 9, 10 and 11 are each associated with FIG. 7 to put to use in an efficient manner, can be used to an advan explain the pressure and temperature controls thereof. tage. Thus the heat of the explosion engine 6 in FIG. 1 which is otherwise largely lost to the atmosphere can be put to use.

DETAILED DESCRIPTION OF THE DRAWINGS AS Stated, in the vapor force device represented in FIG. 1, the evaporator 2 is the heat eXchanger or radiator of an

The novel vapor force device shown in FIG. 1 includes a explosion engine 6 which may be, for example, the radiator Vaporizable fluid 1, an evaporator 2 for vaporizing the fluid, of an automobile or other vehicle, which, instead of being a vapor driven machine 3 which has pistons driven by the cooled with air, is cooled by means of the vapor force engine Vapor, and a closed fluid path 4 in which the evaporator 2 fluid 1 circulating in the closed path 4. The cooling water and the vapor machine 3 are mounted for the transport of the which is pumped through the cooling path 7 of the engine 6 fluid 1. In the closed fluid path 4, upstream of the evaporator by means of the pump 8, and which has a temperature of 2, is mounted a pump 5. The evaporator 2 may in fact be the about 80 C., forms the primary fluid. The fluid which is radiator of a conventional explosion-type engine 6, Such as 15 pumped through the closed path 4 by means of the pump 5 an automobile engine, in which the fluid, Such as water, forms the secondary fluid which is heated until it essentially flows in closed path 7 through the heat eXchanger or radiator reaches the abovementioned temperature and thereby evapo 2 and is pumped by means of pump 8 back to the explosion rates. Downstream of the evaporator 2 is mounted an expan engine 6 to continually cool the engine. The heat of the fluid sion tank 9 in which the evaporated secondary fluid is in closed circuit 7 as it exits from the explosion engine 6 to collected and non-evaporated fluid is collected. Downstream the evaporator 2 may be approximately 240 C. The fluid in thereof is mounted a pressure regulating valve 10 in the the vapor-driven piston-type engine 3 may be of a type that circuit 4. Saturated or preferably Super-heated vapor under vaporizes below 240 C. Such that it will be vaporized by the high pressure is obtained in the evaporator 2. AS indicated heat of the liquid in closed path 7 from the explosion engine above, when tetrafluoroethene is used as the Secondary fluid 6. Thus the invention is characterized in that the fluid 1 is not 25 1 in closed circuit 4, a pressure of 26 bar can be obtained at water, but is a medium which can be easily evaporated and the outlet of the evaporator 2 at 80° C. The pressure at the whose atmospheric evaporation temperature or boiling tem inlet of the vapor machine 3 can be set by means of the perature is lower than 240 C. and preferably lower than 30 preSSure regulating valve 10, for example, as a function of C. in circumstances as will be seen hereafter and which has the pressure in the cylinders of the explosion engine 6. In evaporation characteristics that, even at a low temperature, this way, the explosion engine 6 and the vapor-driven will enable high pressure vapor to be obtained. By “low piston-type engine 3 may be united in one and the same temperature,” it should be understood that such low tem engine block and may possibly even have a common shaft peratures mean below 240 C., as, for example, 240 C., 18 that can be coupled with some driven unit 20 as illus 180° C., 120° C. or 60°, respectively, and the term “high trated in phantom lines in FIG. 1.

preSSure” means a pressure equal to or greater than 10 bar, 35 As illustrated in FIG. 2, the explosion engine 6 and the for example, higher than 20 bar at 120° C., where 1 bar is Vapor-driven piston-type engine 3 may be formed in a equal to 1 atmosphere. common housing 17. The operation of the device is similar Fluids which meet these conditions and which are thus to that disclosed in FIG. 1 wherein the cooling water of the Suited to be used in the device are those fluids which are used explosion engine 6 in closed path 7 passes through evapo in cooling installations Such as fluorohydrocarbons. Suited 40 rator 2, is condensed and is pumped back to the explosion fluids are, for example, fluorohydrocarbons from the Series: engine 6 by pump 8. The heat given up in the evaporator 2 trichlorofluoromethane, dichlorodifluor methane, is applied to the fluid 1 which vaporizes in path 4 and is used chlordifluoromethane, 1,1-dichloro 2,2,2-trifluoroethane, to drive the vapor-driven piston-type engine 3. The con 1,1-dichlor-1-fluorethene, 1-chloro-1,1-difluorethene, 1,1,1, densed fluid at the output of the vapor-driven engine 3 is 2-tetrafluorethene and difluoromethane. Further, Substitutes 45 pumped back to the evaporator 2 by the pump 5 where the such as dichlorotrifluoromethane (for example, KLEAF123 process is repeated. Again, an expansion tank 9 may be of ICI) and tetrafluoroethene (for example, KLEA 134a of placed in the line.

ICI) are interesting. The first mentioned Substance has an In the embodiment according to FIG. 3, the evaporator 2 atmospheric boiling temperature of 27 C. and a critical is not the radiator of the explosion engine 6 but is the temperature of 183 C. under a pressure of 36 bar, whereas 50 explosion engine 6 itself which implies that the explosion the last mentioned Substance has a boiling temperature under engine 6 is mounted in the closed fluid path 4 and the fluid atmospheric pressure of -26 C. but evaporates at 80 C. 1 forms the coolant of the explosion engine 6. Thus, as the under 26.3 bar and at 100° C. even under 39.7 bar. The fluid in closed path 4 is pumped by pump 5 through the critical temperature of this substance is 101° C. under a explosion motor 6, it cools explosion engine 6, is vaporized pressure of 40.5 bar. 55 in the process and is coupled through expansion tank 9 to The vapor is Supplied in an analogous manner as Steam to preSSure valve 10, and thence to the vapor-type engine 3 for a vapor machine with pistons driven thereby. In the vapor driving shaft 18. Both the explosion-type motor 6 and the machine 3, there is a pressure drop. The fluid, under this Vapor-driven piston-type engine 3 may be coupled to the lower preSSure, may have a liquid form and is again pumped common shaft 18 to drive the shaft 18. A bypass feeder loop to the evaporator 2 by means of the pump 5 as explained 60 11 with a pump 12 and a cooler 16 therein is connected to earlier. When the temperature in the evaporator 2 is higher the explosion engine 6 So as to cool off the fluid 1 in closed than the evaporation temperature under the given pressure path 4 in case of a default.

for the vapor machine fluid, a Super-heated vapor is obtained FIG. 4 discloses still another embodiment of the novel and preferably slightly Super-heated vapor is produced in the Vapor driven engine in that the heat for the evaporator 2 is evaporator in order to avoid condensation in the vapor 65 not Supplied by an explosion engine but by a heat Source machine 3. Such Saturated or Super-heated vapor is already such as a burner 13 that heats the operating fluid in fluid path obtained, thanks to the Specially Selected fluid, at relatively 4, by means of a fluid 14 in the evaporator 2 either directly

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or indirectly, as represented in FIG. 4. In the latter case, the is heated to about 120° C. and thus evaporates and is used evaporator 2 forms a heat exchanger with a boiler filled with to drive the Second vapor-driven piston-type engine 22. It a fluid 14 which forms the primary fluid and a pipe or fluid cools off to about 60° C. while driving the second vapor conduit 15 extending through the boiler and which is part of driven piston-type engine 22. This heat can be transferred to the fluid path 4 and through which the operating fluid flows the third vapor engine 24 which is supplied to the third as a Secondary fluid. In this case, the fluid in closed path 4 fluorohydrocarbon, or working fluid, known as R11. This enters the first vapor-driven piston-type engine 20 at a fluid vaporizes at or below 60° C. temperature and drives the temperature, for example, of 180° C. which will drive the third engine 24 and exits the third engine 24 at approxi piston-type engine 20 and vaporize a first fluid in a first mately 15 C. In FIG. 4, the fluid out of the third engine 24 closed System in vapor-driven piston-type engine 20 Such as is transferred back to the evaporator 2 where it is heated disclosed in relation to FIGS 1 and 2. The primary fluid in again to 180° C. and the cycle is repeated. However, in FIG. closed fluid path 4 that exits the first vapor-driven piston 5, each of the Separate fluids in the Second and third engine type engine 20 is at approximately 120° C. and is coupled to 22 and 24 are reheated through the radiators or heat transfer the Second vapor-driven piston-type engine 22 in a heat devices 36 and 37.

transfer relationship therewith. A second fluid flows in a 15 If the fluid used as the first fluid is one that can be heated closed fluid path within the Second vapor-driven piston-type engine 22 that vaporizes at a temperature less than 120° C. to about 240° C. and that cools off to about 180° C. after and thus drives the Second vapor piston engine 22. The engine acan driving vapor-driven piston-type engine, Such vapor piston be placed between evaporator 2 and the first primary fluid in the closed fluid path 4 exits engine 22 at, for vapor piston engine 20 shown in FIGS. 4 and 5 and thus a example, approximately 60° C. and is coupled to the third

Vapor-driven piston-type engine 24 in heat transfer relation unit is obtained with four temperature levels, which, of ship to a third fluid that flows in a closed internal fluid path course, allows for highly efficient use of the heat. Such and which vaporizes at a temperature less than 60° C. to embodimentsexplosion make it possible to increase the output of an engine or other heat Source in a simple manner.

drive the vapor-driven piston-type engine 24. All three engines 20, 22, and 24 are coupled to a common output shaft 25 An efficient engine that can be used as the vapor-driven 18. The fluid in the closed fluid path 4 exits the third piston-type engines discussed in relation to FIGS. 1-5 is Vapor-driven piston-type engine 24 as a liquid which is shown in FIG. 6 in Schematic form. It is known as the pumped by pump 5 back to the evaporator 2 where it is Baudino motor and is patented in France where it carries revaporized and the System repeats itself. publication number FR 2588 645-A1 and national registra FIG. 5 is similar to that illustrated in FIG. 4 except the first tion number 85 15545. (This patent was filed in France on closed fluid path 4 couples vaporized fluid only to the first Oct. 14, 1985 and was made public on Apr. 17, 1987). The Vapor-driven piston-type engine 20 and exits the heat Baudino engine is an anaerobic external combustion engine eXchanger 37, shown in phantom lines, at approximately that uses a combined cycle to co-generate thermal energy 120° C. It gives up essentially all of its heat to the second (cold, heat) and electrical or mechanical energy that can be fluid in the second engine 22. Thus, the first fluid then exits 35 used for any purpose by means of rational utilization of any heat eXchanger 37 as a liquid and is pumped by pump 5 back Source of heat Such as Solar energy, coal, gas, and the like to the evaporator 2, where the process repeats itself. which is first converted into thermal drive power, then into The Second fluid in Second vapor-driven piston-type productive operates, energy. The engine is quiet and clean and using any fuel, in a closed cycle without valves or engine 22 receives essentially most of the 120° C. heat from an ignition System. It can, therefore, meet the Strictest the first stage which is at a Sufficient temperature to vaporize 40 requirements of the new the Second fluid and drive the Second engine. However, after of more than one type ofmarkets requiring the combined use energy Such as heat and electricity, expending this energy driving the Second engine 22, the fluid coupled to the Second heat eXchanger 36 is at approximately and the like by making use of local fuels which existing 60. This heat is transferred to the third fluid in the third engines cannot use.

Vapor-driven piston-type engine 24 where the third fluid is 45 This makes it an attractive alternative for developing vaporized and drives the third engine 24. The second fluid countries where it can compete with Steam turbines and fuel output from evaporator 36 condenses to a liquid and is cells as well as a possible option for many industrialized pumped by pump 28 through closed fluid path 26 back to countries Seeking to conquer new markets. The interchange evaporator 37 where the process repeats itself. In like ability of its components make this simple and tough engine manner, the third fluid in the third vapor-driven piston-type 50 a technology that can be adapted to meet requirements as engine 24 exits the engine in fluid path 30 at approximately different as decentralized electricity generation, and Surface 15° C. as a liquid and is forced by pump 32 back to heat or underwater propulsion.

eXchanger 36 where the process again repeats itself. The In this System, the movement of the pistons is not caused three vapor-driven piston-type engines 20, 22, and 24 are in the same way as in conventional engines, as by internal combined in single housing 100 and are all coupled to the 55 combustion of an air/fuel mixture but by a continuous Series same drive shaft 18 for driving some device 38 such as a of actions performed by two active fluids, a working fluid generator. and a reactivating fluid. These two fluids operate in opposite It is to be understood, of course, that the heat Source 13 directions of flow inside an enclosure between two heat in FIGS. 4 and 5 could be Solar energy, a hot gas, or any Sources at different temperatures Separated by a two-phase other type of energy desired. 60 adiabatic heat eXchanger. The System receives heat from the The fluids of the three individual fluid circuits are adapted outside atmosphere or an external Source, generates power to the temperatures required. Thus, as a first fluid, the that can be used in mechanical, electrical or a thermal form, aforesaid fluoro-hydrocarbon F123 can be used and this fluid and discharges the residual heat to its cold Source. can be heated to 180° C. in the heat exchanger. In the first The System consists of two separate units, an energy vapor engine 20, this fluid cools off to about 120° C. after 65 conversion unit to convert the energy used to thermal energy driving the pistons therein. The Second fluid in the Second and a fluid tight condensation drive power unit to convert the engine 22 is the abovementioned hydrocarbon F134a which thermal energy to thermal mechanical or thermal electric

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energy. The thermal energy conversion chambers adapted to thermal reactivation loop is used either to transfer the heat the energy Source used Such as Solar, oils, waste matter, gas, of the working fluid from the inside of the system to the and the like. This energy Source can be used continuously outside or Vice versa.

Since the movement of the pistons is not connected to the The choice of fluids determine the design technology of injection and the discharge of combustion gases and this the engine and integrate the following parameters: considerably reduces the quantity of harmful gases Such as temperature, preSSure, heat eXchange Surface, need for Sharp nitrogen oxides, carbon monoxide, and the like discharged decompression that does not require over-heating at the to the outside atmosphere by conventional engines. The engine cylinder inputs, and in particular the thermal loops. condensation chamber contains the engine block and the In theoretical terms, an organic fluid containing fluoro, Such driven Systems including compressors, pumps, AC as fluorinet FC75 in the thermal drive loop, would combine generators, fluid tight enclosed fluid/vapor circulation SyS well with freon R11 in the reactivation loop. tems and thermal reactivation circuits. The engine block The use of the Baudino motor in a multi-stage vapor consists of a number of adjacent cylinderS Such as three, powered engine is illustrated in FIG. 7A and FIG. 7B. The each of which contains a piston to transmit mechanical engine 52 comprises three stages 54, 56, and 58, with each power to the drive Shaft. The compression assembly consists 15 stage formed of a Baudino motor. It should be realized that of a number of radially arranged cylinders, three for each Baudino motor is represented by that motor disclosed example, each of which contains a piston that is thermody in FIG. 6 and is shown in FIGS. 7A and 7B with the engine namically coordinated with the adiabatic heat eXchanger and pistons Separated therefrom in order to show the connections that is integral with the reactivation thermal coils. This between the engine pistons and the remainder of the Bau ensures optimal coupling of the engine-compressor assem dino motor. Thus in the first stage, the Baudino motor 54 and bly and operation at constant torque appropriate to the load. the engine pistons 53 are within the same housing as The job of the turbine pump is to ensure constant flow rate represented by the dashed line 51 Surrounding the engine circulation and recombination of the working fluid. pistons 53 and extending from the Baudino motor 54. In like Considering now FIG. 6, under the effect of the heat it manner, engine pistons 55 are an integral part of the Baudino receives, the working fluid in the high-pressure evaporator 25 motor 56 as illustrated by the dashed line 61 surrounding the 41, evaporates thus increasing its pressure and the vaporized engine pistons 55. In like manner, the engine pistons 57 in fluid can then be used to drive the engine pistons 42 the third Stage are formed in the same housing as the cyclically in a well-known manner. An external heat Source Baudino motor 58 as indicated by the dashed line 63 40 may provide the heat to the working fluid in the container Surrounding both of them.

or high-pressure evaporator 41. The evaporated fluid or gas The heat to drive the process of this engine is shown exiting from the pistons 42 is discharged to axial pump 49 derived from a Source Such as a boiler 60 with a burner and heat exchanger 39 where it transfers a part of its heat in system 62 to provide the heat. A fuel such as gas in line 65 closed circulation to the reactivation fluid in fluid path 44. is coupled through a control valve 66 to the burner System Heat exchangers 39 and 46 are integrally formed as one unit. 62. The boiler feed liquid in line 64 in boiler 60 is heated by Thus, gas exiting piston 42 flows through one part 39 in one 35 the burner System 62 and vaporized. A pump 68 pumps the direction and through the other part 46 in the other direction. liquid fluid into the line 64 into boiler 60. A liquid control It is then discharged to the cold Source 43 where it condenses valve 70 is in parallel with the pump 68, so that, as will be and then passes through pump 51 to the heat eXchanger 46 described later, if the valve 70 is opened, the pump 68 is (in the opposite direction than in heat exchanger 39) and essentially disabled to Stop pumping the fluid as needed. returns to its starting point in the closed container 41 for a 40 A liquid level sensor 72 detects the level of the liquid in new cycle. Thus it should be understood that the heat the expansion tank 73 and the boiler 60. The vaporized eXchangerS 39 and 46 are part of an integral unit through liquid is coupled to line 75, where a pressure sensor 74 and which the gas from the pistons 42 passes in the first direction a temperature Sensor 76 give a constant indication of the and then comes back through in the opposite direction as a pressure and temperature of the vapor in the line 75. Thus, fluid through the same heat eXchange unit. Thus the fluid in 45 as can be seen in FIG. 8, a computer may be used to control the high-pressure tank 41, at equal mass, occupies a greater the operation of the various valves and pumps based upon Volume in its vapor phase than in its liquid phase. The the liquid level, pressure, and temperature indicated by the difference in Volume is converted to power that can be used sensors 72, 74 and 76. Thus, at 82 in FIG. 8, the computer by the drive shaft 48 and its latent heat is at least partially fluid level indicator controller receives the liquid level utilized by the thermal reactivation loop fluid path 44. From 50 indication from sensor 72 and sums that signal at 88 with the the heat exchanger 39, the thermal reactivation fluid is preSSure Signal received by the pressure indicator controller coupled in fluid path 44 to a series of compressors 45 and 84 that is derived from the pressure sensor 74. The result of hence by temperature increases, to the adiabatic heat the Summation at 88 is used to control the level control valve eXchanger 46. 70 that bypasses the fluid pump 68 as described earlier. The discharge of the decompressed active fluid from the 55 Thus, if the level becomes too high and/or the pressure engine block cylinders 42 (the decompression is not increases beyond preset limits, the liquid control valve 70 is interrupted, but the fluid is decompressed to equilibrium), opened the proper amount and controls the amount of fluid and the forced recompression of the fluid in part of the heat that pump 68 can continue to supply to the boiler 60. In like exchanger 46, through which the reactivation fluid low manner, as can be seen at step 86 in FIG. 8, the temperature preSSure circuit 44 passes, is caused by the axial pump 49 60 indicator or controller receives the temperature Signal pro which is integral with the turbine 50. The turbine 50, which duced by the temperature sensor 76 and is used by the is mechanically coupled to the drive shaft 48, is partly driven computer through auto Selector 85, in conjunction with the by decompression of the compressed reactivation fluid at 46 preSSure indication at Step 84 to control the pressure control and this compensates for a considerable proportion of the valve 66 that regulates the amount of gas in line 65 being fed power spent on cyclical recombination of the thermal 65 to the burner assembly 62. Thus if the pressure and/or the energy. Depending on the type of application, or the type of temperature becomes too high, the amount of gas being fed combustion chamber used to heat the active engine fluid, the to the boiler to produce that temperature is decreased by

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partially closing control valve 66. All of these controls by controller 126 utilizes that information to operate automatic computer are old and well-known in the art and the operation selector 128 and control bypass valve 112 to allow more of and control of Such valves based upon temperature and the vaporized fluid to be conducted directly to the cooler 96 preSSure Signals is not new in and of itself. by bypassing the Baudino motor piston engine 53 entirely The vaporized fluid in line 75 is coupled to a manually and providing more heat to the third Stage engine 58 as will adjustable valve 78 which may be similar to a needle valve be explained hereafter.

on a carburetor to allow minimum speed control of the In the fluid return line 94 from the second stage Baudino motor. Speed control valve 80 is manually controlled, such motor 56, there is a pump 136 for pumping the fluid back to as by hand throttle or a foot pedal, but of course, could be the first stage engine pistons 53. The engine pistons 53 Serve controlled by a computer, to provide the amount of vapor as the heat Source for the fluid for the Second Stage Baudino necessary to drive engine pistons 53 of the first stage 54 of motor 56. A fluid level sensor 130 on the piston engine 53 the Baudino motor. Thus the vapor begins to drive the gives an indication if there is a fluid buildup in the piston pistons 53 of the first Baudino motor 54 that begin to rotate engine 53. If so, referring again to FIG. 9, the signal shaft 102 which is commonly coupled to all of the stages. generated by the fluid level sensor 130 is used by the The output vapor from pistons 53 on line 89 is used in the 15 computer through level indicator controller 132 to control a Baudino motor 54 as has been explained previously with valve 134 that bypasses pump 136 to control the amount of respect to FIG. 6 and will not be repeated here. The vapor fluid being pumped in line 94 back to the heat source or output from the Baudino motor 54 on line 90 is coupled to piston engine 53.

a preheater 92 which is a heat eXchanger that also receives Considering the Second Stage, the fluid pumped by pump the fluid on line 94 from the second Baudino motor 56 prior 136 (in FIG. 7B) from the second stage Baudino motor 56 to its being coupled to engine pistons 53 as the cooling fluid. passes through the preheater 92 (in FIG. 7A), where, as In addition, the vapor in line 90 that passes through pre indicated earlier, it receives heat remaining in the fluid heater 92 also passes through a cooler 96 by giving up its output from the first stage Baudino motor 54 on line 90 and remaining heat to the fluid 98 from the third stage Baudino is thus preheated. It is then coupled to the engine piston unit motor 58. Thus, the fluid in line 90 gives up its heat to the 25 53 of Stage 1 where it serves as the coolant for Stage 1 and, fluid in line 98 and is cooled itself to a liquid in line 67 where in the process, is vaporized and is output from piston engine it is coupled back to pump 68 and the cycle then repeats 53 in conduit 138 to the second stage engine pistons 55 in itself. Thus, as can be seen in FIG. 9, the manual control 104 FIG. 7B. Again, the temperature and pressure of the vapor (or a computer-controlled signal) controls the speed control in conduit 138 is detected by sensors 140 and 142. If either valve 80 to allow more or less vapor to the piston engine 53 the pressure and/or the temperature exceeds predetermined to regulate the engine Speed. limits, then referring to FIG. 10, the computer, through The pressure and temperature of the vapor in line 75 pressure and temperature indicator controllers 146 and 148, entering piston engine 53 is measured by sensors 108 and utilizes the temperature and pressure indications from Sen 110, respectively. Further, a bypass valve 112, when opened, Sors 140 and 142 to control an automatic selector 150 that allows the vapor to pass through conduit 113 to the cooler 96 35 controls PC valve 144. PC valve 144 is a pressure control for return to pump 68. Thus, referring to FIG. 9, when the Valve that bypasses the engine pistons 55 and couples the preSSure and/or temperature as indicated by Sensors 108 and fluid directly into the Baudino motor 56 of the second stage. 110 are too high or outside normal limits, the computer, as Thus again the pressure and temperature of the fluid that is shown in FIG. 9, through pressure and temperature indicator being Supplied to the engine pistons 55 is controlled. Again, controllers 114 and 116, uses the Sensor Signals indicating 40 the vapor output from piston engine 55 in conduit 152 is abnormal pressure and temperature to drive a controller 118 coupled to Baudino motor 56 which functions as described to control the valves 106 and 112. If valve 106 is opened, the previously in reference to FIG. 6. The fluid output of the Vapor can bypass the engine pistons 53 and go directly to the Baudino motor 56 on line 154 is coupled to a pre-heater 156 remainder of the Baudino motor 54 at a higher temperature. and to a cooler (or pre-heater) 158 where the fluid is If the pressure and temperature are Such that they must be 45 condensed in conduit 160 and is coupled back to pump 136 reduced, then Valve 112 is opened to bypass the entire group for recycling through the Second Stage as described previ of Baudino motors and to couple a predetermined portion of ously. Again, temperature Sensors 162 and 164 are provided the vapor back through cooler 96 where it is condensed to a for the preheater 156 and the cooler 158, respectively. liquid in line 67 and coupled back to pump 68. Thus, not Should these temperatures be indicated to be improper, the only the pressure and temperature of the vapor coupled to 50 computer, using temperature indicator and controller 166 the Baudino motor piston 53 are controlled but also the and 168 in FIG. 10, again using automatic selector 170, pistons 53 can be bypassed entirely or a portion of the vapor controls bypass PC valve 144 to allow the vapor to bypass can be coupled back to the cooler 96 to preheat the fluid from the engine pistons 55 and be supplied directly to the Baudino the second and third stages in conduits 94 and 98. motor 56 in the second stage. Thus the output of the second Further, the temperature at preheater 92 is monitored by 55 stage Baudino motor 56 on line 154 would then have an sensor 120 while the temperature at cooler (or preheater) 96 increased temperature for Supplying to the preheater 156 and is monitored by temperature Sensor 122. If the temperature the cooler 158.

at preheater 92 is below a predetermined temperature as It will be noted that the third stage of Baudino motor 58 determined by sensor 120, then, referring again to FIG. 9, illustrates the details thereof and its connection to the piston the computer utilizes that Sensor Signal through temperature 60 engine 63 in the same manner as illustrated in FIG. 6. As indicator controller 124, and an automatic selector 128 to indicated earlier, each of the Baudino motors 54 and 56 are control PC valve 106 and bypass the engine pistons 53 and likewise constructed. It will be noted that internal pump 172 couple the vaporized fluid directly to the Baudino motor 54, in Baudino motor 58 in the third stage is driven by the shaft thus increasing the temperature on the output line 90. In like 102. Thus in like manner the pump 68 in the first stage and manner, if the temperature of cooler 96 is below a prede 65 pump 136 in the Second Stage may be part of the Baudino termined level, as determined by Sensor 122, then, referring motorS 54 and 56, respectively, in the same manner as again to FIG. 9, the computer through temperature indicator illustrated in Baudino motor 58 in the third stage. However,

Page 11

the pumps 68 and 136 are shown external to Baudino motors be connected to and rotate Shaft 102 to begin circulating the 54 and 56 for ease of explanation. Pump 172 pumps the fluid fluid to the various Stages by the pumps 68 in the first Stage, through line 176 out of the Baudino motor 58 to the cooler 136 in the second stage, and 172 in the third stage. It will be 158 in the Second Stage where it picks up Some heat and also recalled, as stated earlier, that pumps 68 and 136 in the first helps to condense the output vapor from the Second Stage. It and Second Stages, respectively, can be a part of the Baudino continues to the cooler 96 in the first stage where it does the motor as illustrated by pump 172 in the third stage Baudino Same thing and picks up additional heat. It then returns in motor 58. When pressure indicator 74 and temperature conduit 180 to preheater 156 in the second stage where it indicator 76 in conduit 75 to the first stage piston engine 53 picks up more heat from the output vapor of the Second Stage indicate that the input to the System is brought to the in conduit 154 and then is fed into the piston engine 55 as required pressure and temperature, the computer controls the the coolant therefor. As it is cooling the pistons 55, it absorbs gas Valve 66 as explained earlier to maintain the required heat and is vaporized and exits the piston engine 55 in preSSure. Because of the extremely Small Volume of the conduit 182 where it returns to the input of the piston engine liquid in the boiler, this operation takes only a few Seconds. 63 of Baudino motor 58. There it drives the pistons and then The motor 52 is operated at a minimum speed by the passes through the Baudino motor 58 as explained earlier 15 adjusted needle control valve 78 as explained earlier and the and repeats the process. desired Speed is controlled by operation of the manual It will be noted in Baudino motor 58 that a level control control valve 80 to drive stage one. To have a fast balanced valve 174 bypasses pump 172. A fluid level sensor indicator System, Stages two and three can be activated quickly by 184 is associated with the second stage piston engine 55 thus Second Stagebypass controlling

valves 106 in the first stage and 144 in the cause a predetermined amount of the vapor providing an indication when a predetermined fluid level is ized fluid to be transferred immediately to the second and reached in piston engine 55. Then, referring to FIG. 10, the third stages. These bypass valves 106 and 144 are controlled signal from fluid level sensor indicator 184 is utilized by the by the computer through the pressure controllers 106 in FIG. computer and level indication controller 190 to control the 9 and 144 in FIG. 10. They are also controlled by tempera fluid level control valve 174 in Baudino motor 58 to open the ture controllers 166 in FIG. 10 and 192 in FIG. 11 based on valve 174 and reduce the amount of fluid being pumped by 25 the temperature sensors 122 in the first stage and 158 in the pump 172. Thus control can be maintained of the fluid level second stage at the outlet of coolers 96 and 158, respectively, in the piston engine 55 of the Second Stage. from Stages one and two.

It will also be noted that at the output of the piston engine Thus the three preSSures applied to Stages one, two and 55 of the second stage, that there is a pressure sensor 186 and three as indicated by associated pressure Sensors are based a temperature sensor 188. Referring now to FIG. 11, a on the pressures and temperatures of the inputs and outputs pressure indicator controller 190 is controlled by the com of each stage. The pressure control valves 106, 112 and 144 puter to operate an auto selector control 194 to control the are controlled by the computer to bring the System quickly pressure control valve 144 at the input to the Second Stage into balance. Once the stages are in balance, then these piston engine 55 So as to bypass the engine 55 if necessary Valves will be either closed or operated at reduced positions and thus increase the temperature of the fluid that is in heat 35 based on the computer control. transfer relationship with the fluid from the third stage in the The three Stages are individually powered units and the preheater 156 and the cooler 158. Further, fluid level control forces applied to the shaft are required to be balanced. sensor 196 can be attached to the piston engine 57 of the Therefore the speed of the three units may be different and third stage and referring to FIG. 11, the level indicator yet mechanically changed by the inner and outer toothed controller 198, under control of the computer, may operate 40 wheels illustrated by gear boxes 200 and 202 in FIG. 7A and the level control valve 174 in the Baudino motor 58 to FIG. 7B. By mechanically allowing the toothed wheels to bypass pump 172 and thus maintain the proper fluid level in rotate with respect to each other in a well-known manner, the the third Stage piston engine 63. forces applied to shaft 102 are balanced. The pressures on It will be noted that gear boxes 200 and 202 interconnect the pistons and in the lines as determined by pressure Sensors the shaft 102 of the three stages. Thus gear box 200 connects 45 as indicated, indicate the measurements of the power on stages one and two with the shaft 102 while gear box 202 each shaft from each Stage. A computer compares these couples the Second Stage to the third Stage with the output power measurements in a well-known manner and the heat shaft 102. The gear boxes are well-known and have inner flux from one Stage to another is varied by the computer as and outer toothed wheels in engagement with each other and indicated to regulate the Speed of Shaft rotation of the three a respective shaft portion. This will enable forces on the 50 Stages.

shaft from the three Stages to be balanced even if the Speed Because, as indicated earlier, each of the Baudino motors of the three units is different. When the computer controls 54, 56, and 58 utilize a different fluid that boils at a the three Stages to achieve Substantially the same Speed, the temperature less than the output temperature of the preced inner and Outer toothed wheels will Simply rotate together. ing Stage, Stage 2 is receiving Waste energy from Stage 1 and A description of the operation of the multi-stage vapor 55 Stage 3 is receiving waste energy from Stage 2. In the case powered engine 52 shown in FIG. 7A and FIG. 7B is now of needed energy in either Stage 2 or Stage 3 to balance the discussed. During start-up, the boiler 60 and burner 62 are power, Stages 2 and 3 are able to receive additional energy Started with a signal that initiates the following Sequence: through the bypass valves 106 and 144 from stage 1 or stage first, the liquid supply pump 68 is activated and the level of 2 thus controlling the transfer temperature in the preheaters the liquid in the boiler 60 is controlled based on the output 60 92 and 156 and coolers 96 and 158. The computer controls Signal from level Sensor 72 as indicated previously. At the the Overall heat balance to obtain the optimum working Same time, the pilot light of the burner System 62 opens a conditions and the cooling temperatures in coolers 96 and Safety valve in a well-known manner and allows fuel in line 158. The coolers of stage 1 and stage 2, 96 and 158 65 to flow through pressure control valve 66 and is ignited respectively, are designed Such that the maximum heat flux by burner 62. The burner 62 is open to a maximum flow rate 65 during heat transfer periods is taken into consideration. Of which heats up the System and brings it to the required course the coolerS may be oversized to avoid cavitation in preSSure. To commence operation, a Starter motor 204 may the pumpS and to safely cool the liquid.

Page 12

All of the controllers in the systems shown in FIGS. 8, 9, the vapor-driven piston-type engines being coupled to 10 and 11 by the numerals 82, 84, 86, 104, 114, 116, 124, each other Such that the fluid of a preceding vapor 126, 132, 146, 148, 166, 168, 190, 191, 192 and 198 are all driven piston-type engine heats through the intermedi proportional-integral controllers that are well-known in the ary of a heat eXchanger the fluid, which is different, of art and are Such that when the engine functions are noted to the Succeeding vapor-driven piston-type engine have a certain deviation from a Set point as indicated by wherein each of the vapor-driven piston-type engines measurement Signals, the integral function is eliminated. comprises:

The integral function comes back into Service whenever it is an output shaft;

necessary to avoid overshooting in control as is well-known Vapor-driven pistons coupled to Said output shaft; in the prior art. each said vapor fluid inlet receiving a first vaporized To increase or decrease the power or Speed of the motor, fluid from one of the external heat Source, or from a the main Supply valve 66 for the fuel is open to Stage 1 and heat-exchanger connected to this preceding vapor boiler 60. Because temperature and pressure are always kept driven piston-type engine, for driving Said vapor constant at the output of the boiler 60, quick acceleration or pistons and rotating Said output shaft; heavy tracking at low Speed is possible without perturbation 15 a first vapor/fluid path for receiving Said first vaporized of the combustion. Thus the pressure and temperature of the fluid from Said pistons, fluid from the boiler 60 are controlled separately from the an internal pump in Said first vapor/fluid path for preSSure and temperature that are generated by each of the circulating Said vapor/fluid back to Said external heat piston engines 53 and 55 for the three stage motors. The Source for reheating, temperature controllers are in auto Select operation to limit an internal heat eXchanger in Said first vapor/fluid path the temperature of the vapors in the coolers and/or preheat prior to Said external heat Source; CS. a Second closed fluid/vapor path having a Second Thus the present invention relates to a vapor engine that fluid/vapor therein, Said Second fluid/vapor having a has multiple Stages but may be formed in a single block. lower vaporizing temperature than Said first fluid/ Each Stage has it own Separate vapor power Source and the Vapor, Said Second closed fluid/vapor path passing fluids in each Stage are different and have different heat/ 25 through Said internal heat eXchanger to be vaporized; temperature characteristics. In operation, a first fluid passing an internal compressor in Said Second fluid/vapor path through the first stage itself is heated by a boiler to a first and driven by Said output shaft for compressing Said temperature and passes through the first engine Stage. The Second fluid/vapor and raising the temperature first fluid is pumped back to the boiler by a pump. Stage 1 thereof for transfer to Said heat eXchanger; and drives an engine Shaft. ExceSS temperature of the first stage a turbine in Said Second closed fluid/vapor path and is passed to a cooling fluid from the Second Stage. The coupled to Said output shaft and receiving Said cooling fluid of the Second Stage is a Second different fluid Second fluid/vapor and providing power to Said out which, at a Second lower temperature, uses the waste heat of put shaft.

the first stage to drive pistons which are also coupled to the 2. A vapor force engine as in claim 1 wherein it comprises Same Shaft as the first stage. The Second fluid of the Second 35 at least three vapor-driven piston-type engines coupled to Stage passes through an internal heat eXchanger and is each other Such that the fluid of a preceding vapor-driven pumped back to the first Stage for recirculation. A third piston-type engine heats through the intermediary of a heat engine Stage has a third different fluid which passes through eXchanger the fluid of the Succeeding vapor-driven piston the heat eXchangers of both the first and Second Stages where type engine.

it is heated to a third lower temperature than the Second Stage waste heat and then drives the common shaft after which the 40 3. A vapor force engine according to claim 2 wherein it third fluid is pumped back to the Second Stage to be comprises at least a Second heat eXchanger for receiving the recirculated. The three Stages may be mounted one after fluid output from Said first vapor-driven piston-type engine another in a cascade form and be constructed in one unitary to vaporize the different fluid for driving the following of engine block. The fluids in the three circuits are all different Said vapor-driven piston-type engines, a vapor fluid inlet of and are adapted to vaporize at the temperature required by 45 Said Second vapor-driven piston-type engine being coupled those particular engine Stages. Fluorohydrocarbons may be to Said Second heat eXchanger whereby the fluids in each employed as the fluids. Vapor-driven piston-type engine are different and the vapor While the invention has been described in connection izing temperature of the fluid in the Second vapor-driven with a preferred embodiment, it is not intended to limit the piston-type engine is less than the temperature of the fluid of Scope of the invention to the particular forms Set forth, but, 50 the first vapor-driven piston-type engine at the output of this on the contrary, it is intended to cover Such alternatives, engine.

modifications, and equivalents as may be included within 4. A vapor force engine according to claim 3 wherein it the Spirit and Scope of the invention as defined by the comprises three Baudino motors formed by Said vapor appended claims. driven piston-type engines and that comprises: We claim: 55 a first closed path comprising a vaporized fluid line 1. A vapor force engine comprising: coupling the evaporator heated by an external Source to at least two vapor-driven piston-type engines, each of Said the pistons of the first Baudino motor, a line connecting engines having a vapor fluid inlet and a fluid outlet; the vapor output of the Baudino motor to at least one a heat eXchanger or boiler forming an evaporator and heat eXchanger, and a line connecting Said heat being coupled to the vapor inlet and to the outlet of a 60 eXchanger to the evaporator; and first one of Said vapor-driven piston-type engines for a Second closed path comprising a fluid return line con receiving the fluid from said fluid outlet of said first one nected to the outlet of the second Baudino motor, of Said vapor-driven piston-type engines, passing through at least one heat eXchanger, through an external heat Source for Selectively coupling to Said one of Said heat eXchangers in the first closed path, and heat eXchanger or boiler to vaporize the fluid therein for 65 through the housing of the pistons of the first Baudino powering Said first one of Said vapor-driven piston-type motor for cooling them, a line connected to Said hous engines, ing and the pistons of the Second Baudino motor; and

Page 13

a last closed path comprising a return line passing through an internal pump in Said first vapor/fluid path for at least one of the heat eXchangers in the closed path circulating Said vapor/fluid back to Said external heat pertaining to the just preceding Baudino motor and Source for reheating, preferably also through a heat eXchanger in the closed an internal heat eXchanger in Said first vapor/fluid path path pertaining to the preceding Baudino motor and prior to Said external heat Source; through the housing of the pistons of the preceding a Second closed fluid/vapor path having a Second Baudino motor for cooling these pistons, and a line fluid/vapor therein, Said Second fluid/vapor having a connecting this housing with the last Baudino motor. lower vaporizing temperature than Said first fluid/ 5. A vapor force engine comprising: Vapor, Said Second closed fluid/vapor path passing through Said internal heat eXchanger to be vaporized;

at least two vapor-driven piston-type engines, each of Said an internal compressor in Said Second fluid/vapor path engines having a vapor fluid inlet and a fluid outlet; and driven by Said output shaft for compressing Said a first heat eXchanger or boiler forming an evaporator and Second fluid/vapor and raising the temperature being coupled to the vapor inlet and to the outlet of a thereof for transfer to Said heat eXchanger; and first one of Said vapor-driven piston-type engines for 15 a turbine in Said Second closed fluid/vapor path and receiving the fluid from said fluid outlet of said first one coupled to Said output shaft and receiving Said of Said vapor-driven piston-type engines, Second fluid/vapor and providing power to Said out an external heat Source for Selectively coupling to Said put Shaft.

heat eXchanger or boiler to vaporize the fluid therein for 6. A vapor force machine as in claim 5 wherein the fluid powering Said first one of Said vapor-driven piston-type in the evaporator vaporizes at a temperature of less than 180 engines, C. (350 F); the temperature of the fluid at the output of the a Second heat eXchanger for receiving the fluid output first vapor-driven piston-type engine is less than 120° C. from Said first vapor-driven piston-type engine to (248 F.), a vapor fluid of said second vapor-driven piston Vaporize this fluid for driving the Second one of Said type engine being vaporized at a temperature less than 120 Vapor-driven piston-type engines, a vapor fluid inlet of 25 C. (248 F.), the fluid output from said second vapor-driven Said Second vapor-driven piston-type engine being piston-type engine being at a temperature of less than 80 C. coupled to Said Second heat eXchanger whereby the (140°F), and having a third fluid therein that will vaporize fluids in each vapor-driven piston-type engine are dif at a temperature less than 80° C. (140 F).

ferent and the vaporizing temperature of the fluid in the 7. A vapor force machine as in claim 6 further comprising: Second vapor-driven piston-type engine is less than the a fourth vapor-driven piston-type engine having a vapor temperature of the fluid of the first vapor-driven piston fluid inlet and a fluid outlet; type engine at the output of this engine and in that it Said fourth engine having a fourth fluid therein; comprises a third heat exchanger for receiving the fluid Said fourth engine being interposed between Said heat output from Said Second vapor-driven piston-type Source and Said first engine Such that Said heat Source engine and having a third fluid therein that will vapor 35 is coupled between Said fourth engine vapor fluid inlet ize at a temperature less than the temperature of the and fluid outlet for vaporizing said fourth fluid and fluid of the Second vapor-driven piston-type engine driving Said fourth engine; and wherein at least one of Said at least two vapor-driven a heat eXchanger coupled between Said fourth engine and engines comprises, Said first engine Such that the waste heat of the fluid an output shaft; 40 outlet of the fourth engine is used to vaporize Said first Vapor-driven pistons coupled to Said output shaft; engine first fluid and drive Said first engine. each Said vapor fluid inlet receiving a first vaporized 8. A vapor force engine according to claim 7 wherein the fluid from one of the external heat Source, from a fourth fluid in the fourth engine is vaporized at leSS than heat-exchanger connected to this preceding vapor 240° C. (484 F.) at its vapor fluid inlet and the fourth engine driven piston-type engine, for driving Said vapor 45 generates waste heat at its fluid outlet of less than 180 C. pistons and rotating Said output shaft; (350°F).

a first vapor/fluid path for receiving Said first vaporized fluid from Said pistons,