MXPA99001690A - Thermal hydraulic engine - Google Patents

Abstract

A thermal hydraulic engine (7) including a frame (202). A working fluid changes volume with changes in temperature. A working fluid container (130) houses the working fluid. A cylinder (100) secured to the frame (202) includes an interior space. The cylinder (100) also includes a passage (124) for introducing the working fluid into the interior space. A piston (106) is housed within the interior space of the cylinder (100). The working fluid container (130), the interior surface of the cylinder (100), the piston (106), and the working fluid container (130) defines a closed space filled by the working fluid. The engine (7) also includes means (136) for transmitting heat to and removing heat from the working fluid, thereby alternately causing the working fluid to expand and contract without undergoing a phase change. The piston (106) moves in response to the expansion and contraction of the working fluid.

Description

MOTOR HIDR ULICO THERMAL FIELD OF THE INVENTION The invention relates to a motor that is driven by the expansion and contraction of a working fluid as heat is applied and removed alternately from the working fluid. BACKGROUND OF THE INVENTION Typically, energy is not in typically usable forms. There are many ways to convert one type of energy into another. For example, an internal combustion engine can convert the explosive force of a fuel burned into its cylinders into mechanical energy that eventually turns the wheels of a vehicle to propel the vehicle. An internal combustion engine channels energy that results from the combustion of a fuel in a cylinder to a piston.

Without the cylinder and the piston, the energy that results from the combustion of the gas would simply disperse in any available direction. Another example of a device to convert one form of energy into another is a windmill. If connected to an electric generator, windmills can convert the mechanical action of the air into movement in electricity. While an internal combustion engine typically produces mechanical energy from the combustion of fossil fuels, such as gasoline, gas-oil, or natural gas or alcohols, other attempts have been made to produce mechanical energy from the movement of such members. as pistons by means other than combustion of fossil fuels. However, most of these devices still operate on the basic principle of providing a force to drive a moving member, such as a piston.

The difference between the various devices is in the manner in which the force is produced to move the piston and the manner in which the force is controlled. Some of these devices use the movement of a working fluid to drive a moving member, such as a piston. Other devices use the phase change in a liquid to drive a moving member. In operation, some devices use valves to control the flow of a working fluid in the production of mechanical energy by moving a moving member. Due to the growing global demand, the research focuses on ways to produce energy and drive devices that we have in our daily lives. In recent years, another area of research has included alternative sources of energy. Such research has increased steadily. Among the reasons for the increased research is a growing awareness of the limited amount of fossil fuels on earth. This research can also be fostered by an increased desire to provide energy for people who live in remote places around the world, who now live without power. Among the alternative sources of energy on which the research has focused is solar energy. Solar energy has been captured by photovoltaic cells that convert the sun's energy directly into electricity. Solar energy research is also focused on devices that capture the heat of the sun for use in a variety of ways.

As described above, in relation to the examples of internal combustion engines and windmills, the problem that is addressed by both photovoltaic solar cells and solar heating devices is the conversion of one type of energy into another type of energy. In solar cells, the energy of sunlight is used to excite electrons in solar cells, thereby converting the sun's energy into electrical energy. By. On the other hand, in solar energy cells, the sun's energy is typically captured by a fluid, such as solar hot water panels typically seen on the roofs of residences. SUMMARY OF THE INVENTION The present invention has been developed keeping in mind the problem described above. As a result, the present invention relates to a new device for converting one form of energy into another. The present invention may also use to form and / or solar energy sources or other non-conventional forms. Accordingly, the present invention provides a thermal hydraulic motor that utilizes the expansion and contraction of a fluid by alternately transmitting and removing heat from an operating fluid. The energy can provide mechanical and / or electrical energy. An advantage of the present invention is that it can use a variety of heat sources to heat and / or cool the working fluid. Accordingly, another advantage of the present invention is that it is substantially non-contaminating. Along these lines, a further advantage of the present invention is that thermal energy can escape and, therefore, can be powered by solar energy. In addition, an advantage of the present invention is that, since it can be powered by solar energy, it can be used to provide power in remote areas. A further advantage of the present invention is that it can use heat and / or hot water produced by existing processes. Accordingly, the present invention can make use of thermal energy that is not currently used and is disposed of as waste. Still a further advantage of the present invention is that it can operate without fossil fuels. It follows that an advantage of the present invention is that it can produce energy without contributing to the abundance of gases and residual particles emitted into the atmosphere by the combustion of fossil fuels. Furthermore, an advantage of the present invention is that it can include a relatively simple design that eliminates the need for a complex series of valves to control the flow of a working fluid through the system. Accordingly, a further advantage of the present invention is that it provides a simple design, thereby reducing construction and maintenance costs. In accordance with these and other objects and advantages, the present invention provides a thermal hydraulic motor. The motor includes a frame. The engine uses a working fluid that changes the volume as the temperature changes. A reservoir of working fluid houses the working fluid. A cylinder is secured to the frame and includes an interior space. The cylinder also includes a step for introducing the working fluid into the interior space. A piston is housed inside the interior space of the cylinder. The working fluid reservoir, the interior space of the cylinder, the piston, and the working fluid reservoir define a closed space filled by the working fluid. The motor also includes means for transmitting and removing heat from the working fluid, thereby alternately causing the working fluid to expand and contract without subjecting it to a phase change. The piston moves in response to the expansion and contraction of the working fluid. According to additional preferred aspects, the present invention provides a thermal hydraulic motor. The motor includes a frame. The engine also includes a working fluid that changes the volume as the temperature changes. A reservoir of working fluid houses the working fluid. A flexible diaphragm is provided at one end of the working fluid reservoir. The flexible diaphragm moves in response to the expansion and contraction of the working fluid without a phase change in the working fluid. A connecting rod in contact with the flexible diaphragm moves in response to the movement of the flexible diaphragm. The motor also includes means for transmitting and removing heat from the working fluid, thereby alternately causing the working fluid to expand and contract. Still other objects and advantages of the present invention will be readily apparent to those skilled in the art from the following detailed description., wherein only the preferred embodiments of the invention are shown and described, merely by way of illustration of the best contemplated embodiment of the invention. As will be understood, the invention is capable of other different embodiments, and its various details can be modified in several obvious aspects, without departing from the invention. Accordingly, the drawings and description should be considered as illustrative by nature and not as restrictive. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 represents a schematic diagram illustrating an embodiment of a power plant that includes a thermal hydraulic motor according to the present invention. Figure 2 represents a schematic diagram illustrating various components of an embodiment of a thermal hydraulic motor driven by solar energy according to the present invention. Figure 3 represents an aerial view of several components that can be driven by a thermal hydraulic motor according to the present invention, representing the "load" on the motor. Figure 3a shows an embodiment of a chain drive gear and sprocket that can be driven by a thermal hydraulic motor according to the present invention.

Figure 4 represents a schematic diagram illustrating several components of another embodiment of a solar-powered thermal hydraulic motor according to the present invention used to drive a water pump. Figure 5 shows an embodiment of a thermal hydraulic motor according to the present invention that includes three cylinders. Figure 6 represents the various stages of operation of an embodiment of a thermal hydraulic motor according to the present invention that includes three cylinders. Figure 7 shows an embodiment and operation of a thermal hydraulic motor according to the present invention that includes four cylinders. Figure 8 shows the position of a piston at the start of a piston energy stroke of an embodiment of a thermal hydraulic motor according to the invention. Figure 9 shows the location of rotation of a crankshaft in a thermal hydraulic motor according to the present invention, indicating the various positions of the crankshaft with respect to the expansion and contraction of the working fluid and the introduction and removal of the heat from the working fluid. Figure 10 represents a graph showing ranges of operation of temperatures and pressures of a working fluid used in an embodiment of a thermal hydraulic motor according to the present invention.

Figure 11 depicts a cross-sectional view of an embodiment of a heat exchanger for use with a thermal hydraulic motor in accordance with the present invention. Fig. 12 depicts a cross-sectional view of an embodiment of a heat exchanger and working fluid reservoir for use with a thermal hydraulic motor according to the present invention employing mercury as a working fluid. Figure 13 depicts an embodiment of a containment wall for use with an embodiment of a working fluid reservoir according to the embodiment of the present invention. Figure 14 represents a cross-sectional view of another embodiment of a cylinder and piston that can be used in a thermal hydraulic motor according to the present invention. Fig. 14a shows a cross-sectional view of a piston and connecting rod shown in Fig. 14. Fig. 15 shows a cross-sectional view in the foreground of a part of the embodiment of a cylinder and piston shown in the FIG. Figure 14. Figure 16 represents a cross-sectional view of an embodiment of an end of a cylinder of an embodiment of a thermal hydraulic motor according to the present invention, which includes a flexible flange for transmitting the generated force by an expansion of the working fluid to a hydraulic fluid and, finally, to a piston.

Figure 17 shows a side view of an embodiment of a thermal hydraulic motor according to the present invention that includes a cylinder mounted on a crankshaft and pid to a floating anchor that slides inside a guide mounted on a frame. Figure 18 shows the embodiment shown in Figure 17, where the piston is starting its driving stroke and the crankshaft has begun to turn. Figure 19 shows the embodiment shown in Figures 17 and 18, where the piston has started its return stroke and the floating anchor is sliding backwards in its guide. Figure 20 shows a side view of an embodiment of a thermal hydraulic motor according to the present invention that includes two springs to deflect the piston in the direction of its return stroke and a floating anchor shown in Figures 17-19 . Figure 21 shows a side view of an embodiment of a thermal hydraulic motor according to the present invention that includes a frame in which the engine components are mounted. Figure 22 represents a cross-sectional view of an embodiment of a cylinder of a thermal hydraulic motor according to the present invention, in which a heat exchanger is mounted inside the working fluid reservoir. Figures 23A-23H represent cross-sectional views of an embodiment of a thermal hydraulic motor according to the present invention including four radially arranged cylinders, illustrating the engine through several parts of a motor cycle. Figure 24 represents a perspective view of the embodiment shown in Figures 23A-23H. Figure 25A depicts an embodiment of a cylinder that can be included in a thermal hydraulic motor according to the present invention, where the cylinder includes an individual inlet and outlet hole for the passage of a working fluid in and out of the cylinder . Figure 26 shows an embodiment of a cylinder that can be included in a thermal hydraulic motor according to the present invention, where the cylinder includes two orifices for the passage of hydraulic fluid inside and outside the cylinder, in such a way that the stroke piston return is also a drive stroke. Figure 27 shows a schematic view of an embodiment of a thermal hydraulic motor according to the present invention that includes direct heat exchangers instead of heat exchangers for the introduction of heat into the working fluid of the thermal hydraulic motor . Fig. 28 depicts a cross-sectional view of an embodiment of a direct heat exchanger that can be used in an embodiment of the invention shown in Fig. 26. Fig. 29 represents an end view of the direct heat exchanger shown in Figs. Figure 28. Figure 30 depicts a close-up end view of the direct heat exchanger shown in Figures 28 and 29. Figure 31 depicts a cross-sectional view of an embodiment of a mechanical valve that can be used to direct the fluid of working and / or thermal fluid and / or cooling fluid to various parts of a thermal hydraulic motor according to the present invention. Figure 32 shows a cross-sectional view of an embodiment of a crankshaft and a piston crankshaft arm that can be included in a thermal hydraulic motor according to the present invention. Figure 33 depicts a cross-sectional view of the crankshaft shown in Figure 32, showing multiple positions of the crankshaft arm of the piston along a portion of the engine's cycle. Fig. 34 depicts a cross-sectional view of a cylinder of a thermal hydraulic motor according to an embodiment of the present invention that includes a crankshaft shown in Figs. 31-33, illustrating the position of the crankshaft arm of the engine. piston along a part of the engine's cycle. Figure 35 shows a cross-sectional view of another embodiment of a crankshaft and arm arrangement of the piston crankshaft that can be used in a thermal hydraulic motor according to the present invention.

Figure 36 depicts a side view of a moment arm of the crankshaft including reinforcing ribs. Figure 37 shows another embodiment of a thermal hydraulic motor according to the present invention and several associated components including a solar heat collector. Fig. 38 depicts an overhead view of the solar heat collector shown in Fig. 37. Fig. 39 depicts a cross-sectional view of a solar heat collector according to the present invention, including a seasonal tracking chain drive and counterweight. , which shows several positions of the solar heat collector. Figure 40 depicts an alternative additional embodiment of a thermal hydraulic motor according to the present invention. Figure 41 depicts an alternative still further embodiment of a thermal hydraulic motor according to the present invention. Figure 42 depicts an embodiment of a transmission including a steering wheel that can be used with an embodiment of a thermal hydraulic motor according to the present invention. Figure 43 shows an embodiment of a thermal hydraulic motor according to the present invention that includes a piston that is driven both in its drive stroke and its return stroke, includes a passive solar heat collector as a heat source , and operates a water pump; and Figure 44 depicts a further embodiment of a cylinder, piston and crankshaft arm according to the present invention.

Detailed Description of Various Preferred Embodiments of the Invention As indicated above, the present invention is an engine that derives power from the expansion and contraction of a working fluid as the heat is applied and removed alternately from the working fluid. The expansion and contraction of the fluid is transformed into mechanical energy, through the present invention. The mechanical energy can be used directly. Alternatively, the mechanical motor can be transformed into another form of energy, such as electricity. - Accordingly, the present invention includes a working fluid that undergoes volume changes as the temperature changes. Any fluid in a thermal hydraulic motor can be used in accordance with the present invention. However, more energy can be produced from the operation of the engine if the working fluid experiences greater changes in volume over a range of temperatures than fluids that experience less changes in volume over the same temperature range. The present invention operates at least in part on the principle that fluids are not generally compressible. Therefore, according to the present invention, the working fluid does not change shape in another state, such as a solid or a gas during engine operation. However, any fluid that undergoes expansion or contraction with a change in temperature can be used in accordance with the present invention. Among the characteristics that can be considered in the selection of a working fluid are the coefficient of expansion of the working fluid and the speed at which the heat is transferred to the fluid. For example, if a fluid quickly changes the temperature, the speed of the motor can be faster. However, in some cases, a fluid that responds rapidly to changes in temperature may have a low expansion coefficient. Therefore, these factors can be compensated in order to achieve the desired effect for the engine. Other factors that may be considered in the selection of a working fluid include some caustic effects that the fluid may have on the working fluid reservoir, the medium and / or the people working with the engine. A very important factor in determining the size, design, cost, speed and other characteristics of a thermal hydraulic motor according to the present invention is the working fluid. Several fluids have several thermal conductivities and coefficients of expansion, among other characteristics, that can affect the characteristics of the engine. For example, the coefficients of expansion of the working fluid can determine the amount of working fluid necessary to drive the motor. The coefficient of expansion can also produce the amount of heat needed to expand the working fluid. Changing the amount of heat needed to expand the working fluid can change the size of a solar heat collector that provides heat, the size of the heat exchanger that imparts heat, among other factors. In the embodiments of the present invention, in which heat is provided by other energy sources, the amount of energy needed to generate heat to expand the working fluid can be altered based on the thermal expansion characteristics. For example, if a fluid expands to a high degree as heat is imparted, less heat will be required to provide the necessary expansion for the engine. This allows a decrease in the size of the solar collectors, a decrease in the amount of energy needed to expand the fluid or a decrease in the size of the heat exchanger, for example. Figure 27 shows an example of a thermal hydraulic motor that includes a solar heat source. Although the embodiment shown in Figure 27 includes solar heat collectors, a variety of heat sources can be used, or heat transfer or heat exchangers are used. For example, a thermal hydraulic motor according to the present invention can use low grade heat to perform the work. A thermal hydraulic motor according to the present invention can also use medium and high grade sources for fuel. Examples of fuel sources that can be used include natural gas, hydrogen gas, liquefied petroleum gases, gasoline, fuel oils, coal, nuclear, or other fuels. A person skilled in the art would know how to devise a system for imparting heat to the working fluid of the present invention when any of the fuels described above is used. An example of a working fluid that can be used in accordance with the present invention is water. Another fluid that can be used is mercury. Additionally, other substances that can be used as a working fluid include FREON, synthetic FREONES, FREON R12, FREON R23, and liquefied gases, such as liquid argon, liquid nitrogen, liquid oxygen, for example. FREON and related substances, such as synthetic FREONES, FREON R12, and FREON R23 can be particularly useful as a working fluid due to the high degree of expansion they can undergo as heat is introduced into them and the tendency to return to its original volume and temperature after heat removal. Another example of a working fluid that can be used in accordance with the present invention is liquid carbon dioxide. Other fluids that can be used as working fluid include ethane, ethylene, liquid hydrogen, liquid oxygen, liquid helium, liquefied natural gas, and other liquefied gases. Other working fluids can also be used, since a person skilled in the art could determine without undue experimentation once this description is known. In order to capture the energy in the expansion of the fluid, the working fluid is housed within a closed space. The enclosed space can include many different elements. However, the enclosed space typically includes at least one reservoir of working fluid.

Preferably, the working fluid completely fills or substantially completely fills the interior of the working fluid reservoir when the working fluid is in an unexpanded or substantially unexpanded state. In other words, typically, the working fluid is placed in the working fluid reservoir in its densest state, where it occupies the least amount of volume. The working fluid reservoir can then be sealed or connected to other engine components. The volume of the working fluid reservoir depends, among other factors, on the size of the motor, the application, the amount of working fluid required for the application, the amount of working fluid that expands and contracts with temperature changes. The exact interior volume of the working fluid reservoir will be described below with respect to the specific embodiments. However, the embodiments of this type are only illustrative and not exhaustive in nature and, therefore, only represent examples of working fluid deposits. Preferably, the working fluid fluid reservoir is made of a material that can withstand the pressure of the working fluid as the fluid expands. Materials that can be used to form the working fluid reservoir include metals, such as copper, plastic, ceramic, carbon steel, stainless steel, or some other suitable materials that can withstand the temperatures and pressures involved in this specific application. Regardless of the material used, it is preferably not deformable or substantially so when subjected to the forces generated by the expansion of the fluid. The material may change due to the effect of heat but not preferably due to the force of the expansion fluid. The non-deformability of the material from which the working fluid reservoir is made is useful for the transmission of the force of the working fluid expansion to any moving member, such as a piston, which includes the particular embodiment of the present invention. invention. Another voltage to which the working fluid reservoir is subjected results from the heating and cooling of the working fluid. As the temperature of the working fluid increases, the working fluid reservoir may expand, due to the application of heat. Similarly, as the working fluid is cooled, the materials in contact with the fluid will be cooled and may contract. Therefore, regardless of the material used, not only should it be able to withstand the temperatures and pressures of a particular application, but it must also be able to withstand the changes in temperatures and pressures that occur continuously during the operation of an engine. thermal hydraulic according to the present invention. For example, metal fatigue could be a problem in the embodiments in which they are made of metal. However, the fatigue of the metal can be solved by those skilled in the art who can adapt the particular metal to the particular conditions involved in a particular embodiment. Accordingly, it is preferable that the materials in contact with the working fluid, such as the working fluid reservoir, also have some elastic characteristics. A material that is excessively brittle could tend to crack and leak, making the engine inoperative. The number of working fluid reservoirs included in the embodiment of the present invention typically depends on the number of cylinders or other devices used to capture the expansion energy of the working fluid. Preferably, the number of working fluid reservoirs is equal to the number of collection devices of the expansion. However, it can be conceived that there could be more or less deposits of working fluid. For example, an embodiment of the present invention includes a piston that moves back and forth within a cylinder in both directions by expanding the working fluid. One embodiment of this type may include working fluid reservoirs for each cylinder. Therefore, as can be appreciated, the number of working fluid reservoirs in the embodiment of the invention may vary. The working fluid reservoir can be interconnected with a cylinder. Alternatively, the working fluid reservoir can be isolated in a fluid containment system. According to a system of this type, the force generated by the expansion of the working fluid is not transmitted directly to a piston or other mobile member, but is transmitted indirectly. If the working fluid reservoir and cylinder are connected so that the force of the working fluid expansion is transmitted directly to a piston or other moving member, the working fluid container and cylinder can be interconnected in a variety of forms. For example, a tube, flexible tube or other conduit can be used to connect the working fluid reservoir to the cylinder. Alternatively, the working fluid reservoir can be connected directly to the cylinder. Preferably, if the cylinder is connected to the working fluid reservoir with a flexible tube or other conduit, the flexible tube or conduit is also made of a material that resists changes in the configuration as a result of the forces applied by the fluid expansion. of work. An example of a material of this type includes a rubber tube reinforced with steel. As indicated above, the working fluid can be isolated in the working fluid reservoir. According to such embodiments, instead of being transmitted directly to the piston, the force of the expansion fluid can be transmitted to a hydraulic fluid, which then transmits the force to the piston. According to embodiments of this type, the working fluid is housed inside the working fluid reservoir. The working fluid reservoir is in contact with the heat exchanger. However, instead of the working fluid moving from the working fluid reservoir to a cylinder to drive a piston as the fluid expands, the end of the working fluid reservoir that is not surrounded by the exchanger Thermal is closed in a flexible blind flange. In the embodiment shown in Figure 12, the working fluid reservoir and the hydraulic system can be devised to define two sections that form a general fluid containment system. The flexible blind flange 180 can be conceived as an insulator of the working fluid. Therefore, the reservoir of the working fluid 182 in embodiments of this type can be referred to as a fluid insulating section. Another part of the fluid containment system is the hydraulic system 184. The hydraulic system can be thought of as a transfer section that transfers the force of the working fluid to the piston. A fluid containment system is particularly useful if the working fluid is a caustic and hazardous material, such as mercury. The containment and transfer section not only allows a working hazard fluid to be used with the engine, but also allows engine sections to be manufactured and shipped separately and maintained separately. For example, the working fluid reservoir, with or without the heat exchanger 186, could be sent separately from the heat exchanger and the cylinder to which it is interconnected. The fluid containment system includes the flexible blind flange as well as the hydraulic container and other hoses, adapters, tubes and passages that may be necessary to allow the hydraulic fluid to actuate the piston. As described above, the flexible blind flange allows the force of the expansion working fluid to be transmitted to the hydraulic fluid. Without taking into account the components and materials used in the construction of the fluid containment system, it preferably maintains the temperature and pressure of the working fluid. According to one embodiment of this type, a mounting flange 188 extends around the opening of the working fluid reservoir 182. Preferably, the flexible blind flange 180 is then placed on the mounting flange 188 connected to the reservoir. working fluid 182. The hydraulic fluid container can then be fixed on the flexible blind flange. Preferably, the hydraulic fluid container preferably includes a mounting flange 190 having a configuration corresponding to the configuration of the mounting flange 188 on the working fluid reservoir 182. The hydraulic fluid container and the working fluid reservoir can then connect hermetically together in order to seal the space between them, thus preventing the working fluid from escaping from the working fluid reservoir. The hydraulic fluid container is directly connected through one or more conduits to the cylinder. The hydraulic fluid then acts as the working fluid in a different way than it would if it were not isolated in the working fluid reservoir. According to one embodiment of this type, as the working fluid expands, pressure is applied to the flexible blind flange. The flexible blind flange "then applies force to the hydraulic fluid, a pressure is created on the hydraulic fluid, the pressure applied to the hydraulic fluid causes pressure to be applied to the entire surface of the container, cylinder, and piston. The only mobile member in the system moves in response to the pressure Figure 13 shows the retaining wall between the interior of the working fluid reservoir and the interior of the heat exchanger The number of working fluid reservoirs and possibly the containment sections may vary, depending, among other factors, on the number of cylinders and if a power return stroke is used as described below As described above, the working fluid expands and either direct or indirectly, the expansion fluid is directed to a cylinder.The cylinder is at the heart of the invention, since the cylinder houses the piston to which the force of the expansion working fluid is transmitted, thereby moving the cylinder and initiating the mechanical energy produced by the invention. As with the working fluid reservoir and other components of the invention, the cylinder can be manufactured from a variety of materials. The above description related to voltages on the working fluid reservoir and the material from which it is made, is applied to the cylinder. Accordingly, the same materials can be used to form the cylinder. The size of the cylinder may vary depending on the number of factors related to the specific application. Factors that may be important in determining cylinder size include, among others, the number of cylinders, the particular load on the engine, and the amount of energy that must be produced. A typical maximum interior volume size of a cylinder included in a thermal hydraulic motor according to the present invention is from about 350 cubic inches to about 20,000 cubic inches. However, the size of each of the cylinders can vary from about 4 inches in diameter to about 36 inches in diameter. According to one embodiment, an engine with a cylinder having a diameter of approximately 5 inches and a piston stroke of approximately 18 inches generates approximately 10 horsepower. Preferably, the cylinder has a configuration with circular or substantially circular cross section. Figures 5, 7 and 14 illustrate examples of various embodiments of cylinders that can be used in a thermal hydraulic motor according to the present invention. The cylinder can be mounted in a frame onto which other components of the present invention can be mounted. The cylinder can be mounted in the frame in a fixed or articulated manner. Figures 17, 18 and 19 show an embodiment of the present invention in which the cylinder 200 is mounted in the frame 202 in an articulated or pivoted manner. According to this embodiment, the cylinder 200 includes a connecting member 204, such as a fork or other suitable member, which can be pivotably joined to a complementary member on the frame 202. A pin 206 is a means for connecting the cylinder to the frame that can be used. As the piston moves through its cycle and the crankshaft rotates, the cylinder will pivot around its anchor. The embodiment shown in Figures 17-19 also includes a floating anchor. According to this embodiment, the cylinder is pivotally mounted on the anchor until the cylinder can pivot. The anchor is movably mounted within a guide 208. The guide 208 allows the anchor to slide from right to left as shown in Figures 17-19. The guide 208 can be connected directly or indirectly to the frame 202. The floating anchor allows the piston to contract without having to wait for the crankshaft to continue its rotation and without having to overcome other possible forces that tend to act on the piston in one direction opposite to his return race. Without taking into account the embodiment of the present invention, it may include a floating anchor. Figure 20 shows an embodiment of a thermal hydraulic motor according to the present invention that includes springs 210 that deviate and tend to move the piston in the direction of its return stroke. If the engine includes springs, it can include at least one spring. The use of springs to cause the cylinder to move in the direction of its return stroke can be important to maintain a pressure on the working fluid at all times. With some working fluids, this is particularly important, such as with FREON, FREON substituents and analogous compounds. According to the embodiments shown in figures 5, 6 and 7, the working fluid is introduced into one end of the cylinder. Therefore, the cylinders according to these embodiments include only one connection at this end. However, according to other embodiments, described below in more detail, the return stroke, as well as the actuation stroke, is driven by a working fluid. According to embodiments of this type, the cylinder may include means for introducing a working fluid into both ends of the cylinder. Embodiments of this type can also include a seal around a connecting rod attached to the piston, as described in more detail below. Working cylinders of a thermal hydraulic motor according to the present invention may include a hole for the passage of working fluid in and out of the cylinder. According to embodiments of this type, the expansion of the working fluid drives the piston through its actuation stroke. One embodiment of this type is shown in cross section in Figure 25. In this embodiment, the cylinder 326 includes an inlet 328 for the introduction of working fluid into the cylinder. The expansion of the working fluid applies force to the wall of the surface area defining the space 330 into which the working fluid is introduced. As the working fluid spreads, applies force to face 332 of piston 334 located within cylinder 326. Gasket 326 prevents fluid from entering the remaining portion of the interior volume of the cylinder. The force applied to the surface of the piston moves the piston into an extended position, as shown by 338. The piston can be driven on its return stroke by forces created by the contraction of the fluid as well as by forces applied to the crankshaft arm. 340 by other cylinders in a multi-cylinder engine as they experience their actuation stroke or by other forces. Figure 26 shows an alternative embodiment of a cylinder according to the present invention that includes two holes 344 and 346 for the passage of a working fluid in and out of the cylinder. The inclusion of two holes for the passage of a working fluid inside and outside the cylinder allows the piston to be driven in both directions of movement. In other words, the piston constantly undergoes a driving stroke without taking into account the direction of movement of the piston. An embodiment of this type does not require external forces to cause the cylinder to return. A double-bore cylinder also makes it possible to work a piston in two directions. Significantly, a double-bore cylinder can allow a thermal hydraulic motor according to the present invention to operate with a single cylinder. Another benefit of including double-bore hydraulic cylinders in a thermal hydraulic motor according to the present invention is that the size of the motor can be decreased, since the cylinder can provide power to drive a load with the cylinders moving in each direction. Although the motor can be reduced in size, a single cylinder with two holes can not replace two cylinders with a single hole since the hole on the side of the piston where the piston shaft is mounted applies less force to the piston, since the area The piston surface area is reduced to the extent of the area of the tree. An additional added benefit of double-bore hydraulic cylinders is that the flow of working fluid between the cylinders can be interconnected. According to one embodiment of this type, the main orifice, which would be the orifice whose fluid flows in to drive the piston in its actuation stroke in a cylinder that includes only one orifice, such as an orifice 344 in the form of embodiment shown in figure 26, can be connected to a second hole, such as hole 346 in the embodiment shown in figure 26 of a different cylinder. An embodiment that includes interconnected cylinders allows a piston to be pushed by a first cylinder that is driven by fluid flowing into the main orifice and being removed by fluid exiting the second orifice in that cylinder. According to one embodiment of this type, the crankshaft will rotate constantly by the force applied by all the cylinders as the pistons are constantly moving through the working fluid flowing in and out of the first and second. holes simultaneously. A design of this type allows the size of the motor to be decreased. According to one embodiment, a thermal hydraulic motor including two orifices per cylinder can be reduced to almost half the size, compared to a motor that includes individual orifice cylinders. The effect of a double orifice cylinder can be achieved at least partially by using an individual orifice cylinder if a gas is provided on the side of the piston opposite the working fluid. The gas can be pressurized to maintain the pressure balance on the piston when the piston is in a fully retracted position. As the piston moves in its actuation stroke, the gas will be compressed as the working fluid is pushed against the piston. The largest hydraulic force of the working fluid will typically be much greater than the pneumatic force provided by the gas. Therefore, the gas typically will only slightly reduce the forward movement of the piston. As the working fluid contracts, the hydraulic forces on the piston are reduced. The reduced hydraulic forces are typically close in magnitude to the pneumatic forces generated by the gas, thus allowing the gas to help the piston return to the starting position. The design of a chamber, which uses a gas as described above as a spring, can be designed to prevent extreme pressures from developing. The gas pressure should be higher than the hydraulic pressure in the equilibrium position. Additionally, the gas pressure should be large enough to overcome the inertia of the piston and the frictional forces of the O-ring between the piston and the cylinder wall. As indicated above, a thermal hydraulic motor according to the present invention can include only one cylinder. The individual cylinder can be driven by fluid flowing in and out of two holes included in the vicinity of opposite ends of the cylinder. A single cylinder from a hydraulic motor according to the present invention can also include at least one flywheel fixed to the transmission system to allow full rotation of a crankshaft. Figure 42 shows an embodiment of a transmission that can be used with a thermal hydraulic motor according to the present invention. The transmission shown in Figure 42 includes a plurality of gears 800 to multiply the power created by the engine. Steering wheel 802 is on the highest RPM side of the transmission multiplication. The central shaft 804 is the main crankshaft of the engine, which typically operates at a low revolution speed. The gears are mounted on steel plates of 6 inches by 0.5 inches. Also in the embodiment shown in Figure 42, the gears are mounted about 16 inches apart. Of course, a person skilled in the art would use a number of different gears mounted in a different way on different supports. A technician in the field would also connect the gears together and to the engine in a different way. Actually, theoretically, a thermal hydraulic motor according to the present invention would include a single cylinder that only includes an individual hole for the introduction of a working fluid if a flywheel of a sufficient size is provided to allow the rotation of the shaft of crankshaft A person skilled in the art could determine the necessary steering wheel size without undue experimentation based on the description contained herein. A displaceable member piston can be located within the cylinder. An example of a displaceable member of this type is a piston. The movable member will slide back and forth along the length of the cylinder in response to changes in fluid volume as the temperature changes. In order to keep the working fluid in a closed space, preferably, the working fluid is prevented from passing between the cylinder and the piston. This can be achieved by providing a piston having a cross-sectional area only slightly smaller than the cross-sectional area. Furthermore, it helps to secure a seal between the piston and the cylinder if the piston has substantially the same cross-sectional configuration as the cross-sectional configuration of the interior of the cylinder. Any space between the piston and the cylinder can also be sealed by providing a seal around the piston. Alternatively, a gasket may be located on the surface of the piston that faces the interior of the cylinder around the edge of the piston. The seal helps ensure that the space between the piston and the cylinder is sealed. The sealing of the space helps to ensure that any energy that may be derived from the fluid extension is transferred to the piston and is not discarded by leakage of fluid between the piston and the cylinder. If the fluid leaks, it could greatly degrade the performance of the engine. Figures 14, 14a, and 15 show an alternative embodiment of a piston and cylinder device that can be used in an engine according to the present invention. In accordance with this invention, the working fluid is introduced into the cylinder on both sides of the piston 192. Accordingly, the area where the piston and the wall of the cylinder 194 meet is sealed by gaskets 196 and 198 on both sides of the piston. 192. In order to transmit the force from the piston to a crankshaft or other transmission member, a connecting rod can be fixed to the piston. In the embodiments without a driven return stroke, the connecting rod can be connected to the side of the piston opposite the side facing the working fluid, or hydraulic fluid in the embodiments that include a fluid containment system of job. In the embodiments that include a driven return stroke, the connecting rod is still connected to the piston. However, both sides of the piston are in contact with the working fluid.

In the embodiments that include the actuated return stroke, the end of the cylinder whose connecting rod 200 projects, must be sealed by the seal 202 to maintain the working fluid pressure for the actuated return stroke. As shown in Fig. 14a, the force of the working fluid on the side of the piston that is fixed to the connecting rod 200 will be transmitted only to the portion of the piston 192 surrounding the connecting rod. This causes a reduced effective force to be delivered to the crankshaft. This reduction in the service area of the piston can be compensated for by increasing the capacity and speed with which the heat is transferred to the working fluid. Figure 16 shows an alternative embodiment of a thermal hydraulic motor that includes a flexible blind flange. According to this embodiment, the force generated, indicated by the arrows in figure 16, by the expansion of the working fluid applies force to the flexible blind flange 204. The flange then acts on the member 206, thereby displacing the member 206. The movement of the member 206 can be guided by guide 207. Member 206 is interconnected with a crankshaft or other drive mechanism (not shown in figure 16). The flange 204 can be secured between two mounting flanges 208 and 210 in a manner similar to the embodiment shown in Figure 12. Regardless of whether the engine includes a driven return stroke, the connecting rod can be attached in a movable or fixed manner to the piston. If the connecting rod is fixedly attached to the piston, then the cylinder is preferably mounted hinged to the frame. Regardless of whether the connecting rod is attached movably or fixedly to the piston, the connecting rod may include one or more sections. The connecting rod can be connected to a crankshaft and other transmission elements to drive a device or an electric generator. In some embodiments, the cylinder is fixedly attached to a frame and the connecting rod is hingedly connected to the piston and a crankshaft, so that as the piston moves back and forth to Through its stroke and the crankshaft rotates, the connecting rod will change its position. As shown in Figures 23A-23H and 24, the cylinders of the thermal hydraulic motor according to the present invention can be arranged radially. The use of a radial arrangement of the cylinders in the thermal hydraulic motor can allow a more immediate transfer of energy from the cylinders to the crankshaft and any load placed on the engine. Additionally, a radial arrangement of the cylinders can provide a more direct path through the mechanical system of the motor for forces generated by the working fluid. In addition, the return pressure, described in greater detail below, and other internal piston charges and / or piston O-rings can be manipulated more directly by the energy stroke of the engine with radially disposed cylinders. An embodiment of a thermal hydraulic motor according to the present invention including radially disposed cylinders can include any number of cylinders. The number of cylinders in an embodiment of the present invention that includes a radial cylinder device can be an even number or an odd number. The embodiment of the thermal hydraulic motor according to the present invention shown in Figures 23A-23H and Figure 24 includes four cylinders 300, 302, 304 and 306. The cylinders can be fixed to the frame 299. The pistons (not shown) within the cylinders are connected via crankshaft arms 308, 310, 312, and 314 to a connecting member 316. To facilitate rotation of the crankshaft shaft and connecting member 316, the connection between the crankshaft arms 308 , 310, 312 and 314 can be mounted hinged to pistons (not shown) located within the cylinders 300, 302, 304, and 306 or to the connecting member 316. The connecting member 316 can be interconnected through the connecting member. 318 to the crankshaft 320. Figures 23A-23H illustrate the various positions of the pistons, connecting arms, connecting members, and crankshaft through a revolution of the engine, as the cylinders They experience both return and drive races. In Figure 23A, the piston 300 is in its drive stroke. The piston 302 is starting precisely its actuation stroke. Additionally, piston 304 has completed its return or cooling stroke. On the other hand, piston 306 is in the beginning stages of its cooling stroke, or return.

In the view shown in Figures 23A-23H, the crankshaft is rotating in a clockwise direction. The piston 304 has completed its cooling cycle on its return stroke and is starting its heating cycle, but has not yet reached its drive stroke interval. Saying that the piston has not reached its actuation stroke, it is understood that the working fluid has not reached a pressure capable of moving the piston at all or not more than an insubstantial amount along its actuation stroke. In other words, the pressure is not in a range to move the piston and the piston is not physically in the range of its drive stroke. Figure 24 shows a three-dimensional perspective view of the embodiment of the thermal hydraulic motor shown in Figures 23A-23H. As can be seen in Figure 24, the cylinders can be mounted on the frame members 322, 324. The piston mounting frame members 322 and 324 are typically mounted on another structure or structures to secure them. In any embodiment of the present invention, and particularly, in an embodiment that includes a radial arrangement of the cylinders, the cooling cycle of any piston preferably allows the contraction of the working fluid at an equal or faster speed than the extension of the working fluid in a piston that is in its actuation stroke during the return stroke of the piston in question. If the cooling of the working fluid is not as fast as the increase of the temperature in the working fluid, the working fluid can create a "counter-pressure" which can reduce the movement of the piston in its actuation stroke. The counter-pressure can create an unnecessary load on the motor, preventing the entire operation of the motor. This is particularly the case in an embodiment of an engine according to the present invention that includes a radial cylinder device, since the cylinders are typically arranged in opposite pairs. If a cylinder experiences a counter-pressure as a result of a less rapid cooling and contraction of the working fluid, when compared to the heating and extension of the working fluid, in another cylinder that undergoes its actuation stroke at the same time, the cylinder that is subjected to its actuation stroke will be inhibited in its movement by the counter-pressure. As such, the counter-pressure acts as an additional load on the motor in addition to any load, such as a pump or other device that the motor is driving. One way to help prevent the existence of counter-pressure is to ensure that the heat is removed from the working fluid in a sufficiently fast manner. This can be achieved by ensuring a flow of cooling fluid sufficiently fast to result in the removal of heat from the working fluid in the cylinder that is subjected to a return stroke at a speed equal to or greater than the transmission of heat to the fluid of work on the cylinder that is subjected to a drive stroke. If, as described herein, the engine does not include heat exchangers, then preferably, the rate of heat transfer from the working fluid to the cylinder that is subjected to the return stroke is equal to or greater than the heat transfer rate to the working fluid in the cylinder that is subjected to the actuation stroke. The elimination and transmission of heat may depend on the characteristics of the working fluid, the source of cooling source, the heat exchanger, among other factors. The transmission elements are then connected to a load to perform a desired function. For example, the engine could operate a water pump, an electric generator, and / or a FREON compressor, among other elements. In order to transmit heat and remove heat from the working fluid, the working fluid reservoir is preferably in communication with means for transmitting heat and removing heat from the working fluid contained in the working fluid reservoir. The same means can carry out both heating and cooling. Alternatively, the present invention would include separate means for performing each function. According to one embodiment, the means for transmitting heat and for removing heat from the working fluid are a heat exchanger. Depending on whether it is desired that the working fluid be heated or cooled, water or other relatively hotter or relatively cooler material may be introduced into the heat exchanger. Preferably, a thermal hydraulic motor according to the present invention includes a hot exchanger for each working fluid reservoir, although an engine according to the present invention could include any number of heat exchangers. Figure 11 shows an embodiment of heat exchanger or working fluid reservoir according to the present invention. According to this embodiment, the working fluid reservoir 176 is surrounded by the heat exchanger 178. This heat exchanger includes two openings, one inlet and one outlet. A relatively hotter or colder material may be introduced into the heat exchanger to heat or cool the working fluid. Whether the working fluid is heated or cooled depends at least in part on whether the material in the heat exchanger is relatively hotter or colder than the working fluid. The working fluid reservoir may include a plurality of fins or other devices for increasing the surface area of the working fluid reservoir in contact with the material introduced into the heat exchanger. Other alternatives to increase heat transfer to the working fluid include a circulation pump in the working fluid reservoir.

A circulation pump can create turbulent flow for increased heat transfer rate. The heat exchanger is an example of a means to transmit heat or remove heat from the working fluid. The heat exchanger can be formed around the working fluid reservoir whether it is part of a containment system or not. In a heat exchanger, typically, high and low temperature fluids are contacted with the working fluid reservoir. Typically, the fluid circulating through the heat exchanger is under relatively low pressure. However, the working fluid changes the temperature, depending on whether it is desired to heat or cool the working fluid. Therefore, the heat exchanger is preferably further constructed of a material capable of withstanding the pressures and temperatures that are circulating through the fluid. Examples of materials that can be used in the heat exchanger are polyvinyl chloride tubing (PVC), metal tube such as carbon steel, copper, or aluminum, molded plastic injected or cast, or a combination of materials capable of withstanding the pressures and temperatures involved in the heat exchanger. It is not necessary that only a liquid is used in the heat exchanger to transmit heat or to remove heat from the working fluid. For example, gases or a combination of liquids and gases can also be used in the heat exchanger to heat and / or cool the working fluid. An advantage of the present invention is that any source material of high and low temperature, both liquids, gases or transmitted by other means, can be used to heat and cool the working fluid. For example, wastewater heated from industrial processes could be used to transmit heat to the working fluid. Water of this type is typically chilled in some way before it is discharged into the environment. Therefore, instead of being discarded, the heat in this water could be used in the present invention to produce electrical and / or mechanical energy. As indicated above, solar heating and cooling could also be used in accordance with the present invention. It is this ability to utilize heat and cooling from unused sources, such as residual heating, or free sources, such as the sun, which makes the present invention so desirable. If a fluid is used in the heat exchanger, preferably, the liquid and / or gas would be under at least some amount of pressure to ensure that liquids and / or gases flow through the heat exchanger. As the liquid and / or heated gas moves through the heat exchanger, it will transfer its higher heat energy to the working fluid that has lower heat energy. The working fluid will then expand, applying force against a piston, flexible barrier or other member, thus producing mechanical energy. When the working fluid has absorbed as much heat as possible or as desired from the heat exchanger, a relatively cooler liquid and / or gas can be transferred through the heat exchanger. The heat in the working fluid will then flow according to natural laws, to the relatively liquid and / or coldest gas in the heat exchanger. Fig. 22 shows an alternative embodiment of a heat exchanger according to the present invention. According to this embodiment, the heat exchanger 212 is located within the working fluid reservoir 214. According to this embodiment, the working fluid reservoir is also continuous with the piston. According to other embodiments that include the heat exchanger within the working fluid reservoir, the working fluid reservoir may not be continuous with the cylinder. In figure 22, a distance 'a' represents the displacement of the piston between its maximum positions in the drive and return stroke. The end 216 of the working fluid reservoir 214 can be sealed with a flange 218 secured between a flange 220 on the working fluid reservoir and an end flange 22 secured to the working fluid reservoir flange 220 with pins 224. The figure 5 shows a simple version of a three-cylinder engine according to the present invention. The components shown in Figure 5 may not necessarily be in the same physical position in relation to each other in the engine and are shown here in this arrangement for ease of understanding. The engine may also include other components not necessarily included in these embodiments or shown in this figure. The motor shown in Figure 5 includes three cylinders 100, 102 and 104. A piston 106, 108, and 110, respectively, is disposed within each of the cylinders. Each of the pistons is connected to a connecting rod, 112, 114 and 116 respectively, which is connected to a crankshaft 118.

The number of cylinders and pistons included in the invention may vary, depending on the embodiment and factors described above. An engine using a piston such as that shown in Figures 14 and 15 can use only two cylinders and pistons since the pistons will be pushed into the cylinder by the working fluid that enters the side of the cylinder where the piston is fixed to the piston. connection rod. This is because there is less need to maintain engine speed to ensure that the pistons will move within the cylinders that is needed when a drive and return stroke is not used. Therefore, without using the drive return stroke and only using the forward drive stroke, it is preferable that the motor includes at least three cylinders. Due to the slow-moving nature of the pistons in an engine according to the present invention, it may be necessary to include three pistons to ensure that the pistons will complete their return stroke. With three pistons, at least one piston will always be in a drive stroke, to help ensure that another piston will help complete its return stroke. This occurs because a piston that is always in the drive stroke will promote the rotation of the crankshaft shaft thereby helping to move the other pistons along their return stroke. However, an engine according to the present invention It can include any number of cylinders. For example, motors with 16, 20, or more cylinders can be formed for operations of larger electric power plants. The crankshaft is interconnected with a load. The load could be a mechanical device driven by the crankshaft. Another example of a load could be an electrical generator that is driven by the crankshaft. The crankshaft is also connected to a water valve 122 which controls the flow of gas and / or high and low temperature liquid inside the heat exchangers. The cylinders 100, 102, and 104 are interconnected to each other through a high pressure flexible tube, 124, 126 and 128, respectively, to a working fluid reservoir 130, 132, and 134, respectively. The working fluid reservoirs 130, 132 and 134 are enclosed within heat exchangers 136, 138 and 140, respectively. The working fluid may be contained within the space defined by the heat exchangers 130, 132, and 134, the high pressure connectors 124, 126, and 128 and the interior of the cylinders 100, 102, and 104. Of course, in For embodiments that include a fluid containment system, the working fluid is contained within the working fluid reservoir. As is evident, in the embodiments without the working fluid containment system, the space in which the working fluid is contained changes in volume as the piston moves inside the cylinder. Figure 6 shows a series of representations of the three-cylinder engine shown in Figure 5 as the cylinder cycle. In the embodiment shown in FIG. 6, 141 represents an off-center lobe cam with oscillating arm lever and / or push rods for pushing open water valves. The camshaft controls the flow of heat and cooling to the working fluid. Each working fluid / heat exchanger / cylinder reservoir is represented by 1, 2, and 3. The heating and cooling flow is represented by high temperature water flow within the system 142, low temperature within the system 144, return of high temperature 146, and low temperature return 148. The flow from the high temperature source to the system is represented by 150, the low temperature flow from the low temperature source to the system is 152, the flow from the system until the source of high temperature is represented by 154, and the flow from the system to the low temperature source is represented by 156. As the cylinders run in cycle as shown in Figure 6, the high and low temperature fluid flows in and out of the heat exchangers depending on whether the particular cylinder involved moves in one direction or another. As shown in Figure 5, the opening and closing of the valves directing high and low temperature fluid within the heat exchanger can be controlled by a camshaft connected directly or indirectly to a camshaft driven by the cylinders. An indirectly connected camshaft could be connected to the crankshaft with a timing chain type connection. Of course, any connection could be used to connect the camshaft to the crankshaft. The camshaft could be an off-center lobe cam with oscillating arm lever and / or push rods to push open water valves leading to the heat exchangers. Figure 7 shows an embodiment of a thermal hydraulic motor according to the present invention including four cylinders 158, 160, 162, and 164. Valves 166 and 168 that transmit hot and cold fluid to and from the heat exchanger they are controlled directly by the crankshaft 170. In Fig. 7, the piston 158 is in the process of starting its actuation stroke. Hot fluid is flowing into the heat exchanger 172 associated with the piston 158 and is also being removed from the heat exchanger 172. The circulation pumps can be operated directly from the drive of the crankshaft directly or indirectly. The indirectly driven circulation pumps could be driven by motors and / or hydraulic pumps. The cooler fluid, in this case water used to cool the working fluid, can be obtained from water pumped from a well by the engine. As seen in the embodiment shown in Figure 4, the engine, through a transmission, drives a pump that pumps water from a water source, such as an underground well. An embodiment such as that shown in Figures 2 and 4 can be self-sufficient and does not require any external power. Of course, an embodiment of this type could be connected to a power line to operate the pump during insufficient light times, either during cloudy days or at night. Alternatively, batteries could be provided to drive the circulation pump at such times. Figure 1 shows a general schematic drawing of a power plant using a thermal hydraulic motor according to the present invention. In general, a power plant of this type includes a high temperature source 1, a low temperature source 3, a heat exchanger 5, a thermal hydraulic motor 7 which, in this case, refers to the working fluid and the cylinders themselves, a transmission 9 of some kind, perhaps a flywheel 11 to maintain the momentum of the engine, and an electric generator 13. Of course, the power plant does not necessarily have to include a flywheel and does not need to derive an electric generator . The power plant could also include additional components not shown in Figure 1 and / or not included in the embodiment shown in Figure 1. Figure 2 shows an embodiment of a thermal hydraulic motor that uses solar energy to provide heat to heat the working fluid and an evaporative cooling system to remove heat from the working fluid. Figure 2 illustrates the flow of heating and cooling water through the various components of the system. Of course, a material other than water can be used to heat and cool the working fluid. As the cooling water enters a heat exchanger associated with a cylinder, to suck heat out of the system, the hot water that is created as the cooling water absorbs heat from the working fluid can be recirculated to a hot water tank, if the system includes a tank. The system shown in Figure 2 includes solar panels of hot water 2 to heat the water that will cause the expansion of the working fluid. The water heated by the hot water panels will flow through at least one water direction valve 4 which directs the hot water to a hot water tank 6. From the hot water tank 6, the heated water will flow to a pump of hot water 8. The hot water pump 8 will circulate the hot water to the thermal hydraulic motor (not shown) and then back to the hot water solar panels 2 that must be heated again. The embodiment shown in Figure 2 also includes an evaporative cooling system 10 to provide water that is cooler than the water heated by the hot water solar panels 2 to remove heat from the working fluid. The water cooled by the evaporative cooling system 10 flows out of the evaporative cooling system through at least one water direction valve 4. The water direction valve directs the chilled water to a cold water tank 12. From the cold water tank 12, the chilled water will flow to a cold water pump 14. The cold water pump 14 will circulate the chilled water to the thermal hydraulic motor (not shown) and then back to the evaporative cooling system 10 to be cooled again.

Figure 3 shows an embodiment of the interconnection between the crankshaft 15, driven by the thermal hydraulic motor (not shown in Figure 3), and the elements that form the load on the engine. In this embodiment, the crankshaft shaft 15 is connected to a chain drive gear and toothed wheel 17 which includes two relatively large gears 19 and 21 connected lastly to a smaller gear 23. As can be seen, the rotation of the The crankshaft 15 will be greatly amplified by the gear in the embodiment shown in Figure 3. Figure 3a shows an enlarged side view of the chain drive gear wheel 17, which shows the gears 19, 21, and 23 and the chains 20 and 22 driven and driving the gears. The chain drive gear can be connected to a hydraulic pump 25 and motor multiplier gear 27 which is ultimately connected to an electric generator 29. A flywheel 31 can be interconnected between the hydraulic pump and the motor multiplier gear to assist to maintain the motor cycle. Figure 4 represents a schematic view of another embodiment of a solar-powered thermal hydraulic motor and some associated elements according to the present invention. The heat is supplied and eliminated from the working fluid by relatively hotter and colder water. As with any embodiment, a material other than water can be used to supply heat and remove heat from the working fluid. Figure 4 also shows the flow of hot water through the system.

The embodiment shown in Figure 4 includes the thermal hydraulic motor 33. The solar panels 35 provide the heat that heats the working fluid in the engine. The heated water is then moved to a series of valves 37, 39, 41, and 43. The number of valves may depend on the number of cylinders in the engine, the number of heat exchangers, and how the water is distributed to the exchangers of heat and cylinders, among other factors. The valves 37, 39, 41 and 43 supply the water to the heat exchanger (s) 45. The heated water then heats the working fluid in the motor 33. After supplying its heat to the working fluid, the water heated is directed through the valves 47, 49, 51 and 53 and then returns to the solar arrangement 35. A circulation pump 55 drives the hot water flow. The circulation pump 55 can be driven by electricity generated by photovoltaic cells (not shown). The thermal hydraulic motor 33 can be connected to the transmission 57. In this embodiment, the motor 33 drives a pump 59. The pump 59 can be used to pump water from a water source 61. The water source 61 can include a well , deposit, or tank, among other sources. The water can be pumped from the water source 61 into a water storage pipe 63. The water from the water source 61 can be used as the source of cooling water to cool the working fluid as well as a source of water that it must be heated to provide heat to the working fluid. The water for any function can be stored in a storage tank 63. The engine components according to the present invention can be mounted on a frame. Figure 21 shows an embodiment of a thermal hydraulic motor according to the present invention including four cylinders where the engine components are mounted on a frame A. To simplify the explanation of the operation of the present invention, the operation will be described of a three-cylinder engine according to the present invention. Figure 5 shows an example of an embodiment of this type. The working fluid is contained within the cylinder and the working fluid reservoir is surrounded by the heat exchanger. ThusIn one sense, the heat exchanger acts as a containment system. Due to the fact that there are three cylinders 67, 69, and 71 and three pistons 73, 75, and 77 in the embodiment described here, each piston preferably drives the crankshaft 79 about a turn of at least 120 °, so that a piston is always in operation by actuating the rotation of the crankshaft. The operation of the engine will be described in the assumption that a piston will initiate its actuation stroke. To start the drive stroke, the working fluid must be heated. The embodiment shown in Figure 5 includes three hot exchangers 132, 136, and 138 to introduce heat and remove heat from the working fluid. The difference between the working fluid in a hot state and a cold state can vary, depending on the embodiment. According to one embodiment, the difference between the high temperature of the working fluid and the low temperature of the working fluid is approximately 40-60 ° F. However, the difference between the high and low temperatures of the working fluid may be higher or lower. The high temperature of the working fluid can be any from about 80-200 ° F. The temperature range of the high temperature of the working fluid can also be from about 120-140 ° C. However, any temperature for the high temperature of the working fluid could be used as long as it is higher than the lower temperature of the working fluid. In fact, superheated water above 212 ° F could also be used. The low temperature of the working fluid may vary from about 35 ° F to about 85 ° F. According to one embodiment, the low temperature can be from about 70 ° C to about 85 ° C. However, as indicated above with respect to the high temperature, the low temperature of the working fluid can be any temperature, provided it is lower than the high temperature of the working fluid. The greater the difference in high and low temperatures, the greater the possibility of heating and cooling the working fluid. The temperature of the working fluid can also be defined by defining the maximum temperature of the working fluid with respect to the minimum temperature of the working fluid. Accordingly, the difference in temperatures of the working fluid can be up to about 60 ° C. Alternatively, the difference in working fluid temperatures may be between about 60 ° C and about 120 ° C. Other ranges for the difference in working fluid temperatures include between about 120 ° C and about 180 ° C and between about 180 ° C and about 240 ° C. Before the start of operation of the engine, the working fluid can be pressurized to help maintain a seal between the piston and the cylinder wall. A positive pressure maintained in the cylinder can help force a seal in the area between the piston and the cylinder. For example, the working fluid could be pressurized to approximately 200 lbs per square inch. If the working fluid is pressurized, it can be pressurized to such an extent that during the contraction of the working fluid as the heat is removed from the working fluid, the pressure inside the cylinder never falls below 0. However, no it is necessary that the working fluid be pressurized at all. Figure 10 shows a graph showing the operating range of temperatures and pressures as an embodiment of a thermal hydraulic motor using a working fluid. As the working fluid heats up and begins to expand, the force of the fluid is transmitted to the piston, thus moving the piston. According to an embodiment of the present invention that includes three cylinders, the rotation of the crankshaft does not begin until the connecting rod 174 has moved to a point approximately 20 ° beyond the upper dead center, as shown in Figure 8. As indicated above, in one embodiment of three cylinders, the piston must drive the crankshaft shaft at least 120 ° since there are three pistons and 360 ° in a full turn of the crankshaft. Similarly, in a four-cylinder engine, each piston must drive the crankshaft about 90 °. The corresponding number of degrees that the piston must drive the rotation of the crankshaft can be calculated simply by dividing 360 ° by the number of pistons. Due to the fact that the crankshaft rotation does not start until the connecting rod has moved approximately 20 ° beyond the upper dead center, the calculation of the 120 ° of the piston drive stroke will be calculated from this starting point of the 20 ° turn. However, the driving stroke of the next piston will start after the connecting rod reaches 120 ° beyond the upper dead center. Therefore, there will be a 20 ° overlap between the actuation stroke of the first cylinder and the second cylinder. This will help ensure a smooth transition between pistons, the effective turning force being transmitted to and from the crankshaft being kept completely constant. The uniform power transition is facilitated by the fact that as any piston moves through its drive stroke, it not only drives the rotation of the crankshaft or other device that takes advantage of the movement of the piston, but it also helps to drive the other pistons in the motor on its return stroke. As shown in Fig. 9, the heat source associated with the first cylinder is preferably cut off when the connecting rod reaches approximately 120 ° beyond the upper dead center, in accordance with this embodiment. Next, the source of cold fluid starts inside the heat exchanger when the connecting rod reaches approximately 140 ° beyond the upper dead center. As the return stroke of the first piston continues and the rotation of the connecting rod and the crankshaft continues, when the connecting rod reaches approximately 300 ° beyond the upper dead center, the source of cold fluid towards the exchanger of heat closes and the high temperature fluid source to the heat exchanger starts again. The points at which the high and low temperature fluid sources are introduced into the heat exchanger may vary, depending on the embodiment of the invention. A factor that can alter the flow of the high and low temperature fluid within the exchanger is whether or not the working fluid is pre-pressurized, as described above. The speed of movement of the piston and, therefore, of the crankshaft can be increased by increasing the flow of high temperature fluid within the heat exchanger. The speed of operation of the engine and the output of horsepower can also be increased by increasing the temperature differential between the high and low temperature fluids introduced into the heat exchanger and, therefore, the working fluid. At the 300 ° pivot point, when the high temperature fluid source is reintroduced into the heat exchanger, the working fluid has returned to its base temperature, pressure and volume. It is these volume, temperature and pressure parameters that are used to calculate the motor size, the high and low temperature fluid flow to the heat exchanger, the motor load, the cylinder size, the number of cylinders, and many other parameters of design and operation of the invention. The high and low temperature fluid flow within the heat exchanger described above can be controlled in a variety of ways. For example, a timing gear can be connected directly or indirectly to the crankshaft. The timing gear can mechanically actuate valves that control the high and low temperature fluid flow within the heat exchanger based on the position of the crankshaft. Alternatively, a cam shaft rotated by the crankshaft may operate an electrical system that electrically controls the flow of high and low temperature fluid within the heat exchanger. Other methods that may be used to control high and low temperature fluid flow within the heat exchanger may include lasers, computer programs, optical devices, mechanical push rods, connecting rods, levers or other manual and / or automatic devices . As will be appreciated, a complex computer control could optimize the operation of a thermal hydraulic motor according to the embodiment, just as electronic control has helped to optimize the operation of internal combustion engines in modern automobiles. A modern electronic control system can simultaneously monitor and control a wide variety of parameters, which optimize the operation of the motor. As indicated above, the thermal hydraulic motor of the present invention may include a mechanical valve to direct the flow of working fluid and other fluids. Figure 31 shows an example of a rotary valve that can be used to direct the work flow and / or coolant in a thermal hydraulic motor according to the present invention. The valve shown in Figure 31 includes a connector 560 connected to a valve body 562. The valve body houses a valve rotor 564 that rotates within the valve body. The rotor valve 564 includes a plurality of outlets 566, 568, 570, and 572. The valve body 562 can be connected to an anchor block 574 or other structure for securing the valve. The valve body and the valve rotor can be maintained by a cap 576. The valve body 562 further includes outputs 578, 580, 582 and 584. The outlets 578, 580, 582, and 584 are connected to outlet tubes 586, 588, 590, and 592. The valve body outlets 578, 580, 582, 584 are also aligned with the rotor valve outlets 566, 568, 570, 572, so that as the valve rotor rotates and the outlets 566, 568, 570 and 572 are aligned with the outlets of the valve body 578, 580, 582, and 584, the coolant, the working fluid or other fluids will flow to the desired location. The valve rotor 564 can be rotated through the geared operation of a timing chain connected to the main shaft of the crankshaft. The embodiment shown in Figure 31 includes sprockets for connection to the timing chain. Instead of the rotary valve, the flow of fluids in the present invention can be controlled mechanically with the use of other types of valves, including oscillator arm / pushrod / cam time mechanisms. The flow of fluids can also be controlled with an electric solenoid valve. Any other valve can also be used to direct the flow of fluids in the present invention. Additionally, a turn-on valve such as that shown in Figure 31 can be included in any engine according to the present invention. The thermal hydraulic motor according to the present invention may include a crankshaft system of the piston engine operating independently of each other. In typical engines designed in-line, V-shaped, or radially, each piston is mechanically connected to each of the other pistons. Internal combustion engines use this mechanical dependence to push exhaust gases out of the engine, push fresh gas into the piston chamber, and pressurize the gas before combustion. However, less mechanical dependence may be required in a thermal hydraulic motor according to the present invention.

For example, if the cylinders include two holes, the mechanical interconnection of all the pistons may not be necessary. The return of the piston in such systems is typically achieved most often by pressurization of the opposite side of the piston. This return mechanism also supplies the driving energy of the crankshaft. The present invention can utilize a crankshaft that can be rotated by a free-throw arm mechanism that is capable of freely sliding around the crankshaft in a return direction, locking on the crankshaft in a forward or reverse direction. drive. Figures 32-35 show an example of a crankshaft of this type. The crankshaft shown in Figures 32-35 includes a ratchet type mechanism. The shaft shown in Figures 32-35 can be used in combination with multiple crankshaft arms to provide a turn shaft continuously. Figure 32 shows a crank arm 587 connected to a crankshaft 589. The crankshaft 589 includes an indentation 591 that receives a portion of the crankshaft 587. As can be seen in figure 32, the crankshaft arm 587 will cause a turn of the shaft 589 to the point that the crankshaft arm 587 moves out of the recess 591. Preferably, the crankshaft arm 587 will no longer engage with the recess 591 at a point substantially near the end of the drive stroke of a piston connected to the crankshaft arm 587, so that the power of the piston communicates substantially and completely to the crankshaft 589. The crankshaft arm 587 will then be mounted along a surface of the crankshaft 589 while the piston is in its return stroke. When the piston begins its actuation stroke again, the crankshaft arm 587 will then begin to move along the surface of the crankshaft until it engages a recess. Figure 33 shows an embodiment of a ratchet type crankshaft illustrating the position of a crankshaft arm through a piston driving cycle. Figure 34 shows an embodiment of a cylinder, crankshaft arm, and crankshaft including a ratchet type movement mechanism. Figure 34 also illustrates the various positions of the crankshaft during the movement of the piston. Figure 35 shows another embodiment of a crankshaft and crankshaft arm using a ratchet type mechanism. Fig. 36 shows a crankshaft moment arm including reinforcing ribs 599 to reinforce the crankshaft moment arm to thereby ensure that it can withstand the large pressures generated by the present invention. Instead of relying on heat exchangers, heat can be imparted to the working fluid directly. An example of an embodiment of the thermal hydraulic motor according to the present invention that includes direct heat transmission to the working fluid is shown in Figure 27. The embodiment shown in Figure 27 includes four radially disposed cylinders. The motor includes a centrally located rotation valve 360 to which each cylinder is connected. Each cylinder is also connected to a working fluid reservoir to which heat is directly imparted. By directly heating the working fluid, a heat exchanger is not used and the heated liquid is not used to transfer heat from a heat source to the working fluid. The direct transfer method directly heats the working fluid with the heat source. As can be appreciated, there is no heat loss associated with the use of heat exchangers. Figure 28 provides an example of an embodiment of a working fluid reservoir that can be used in a hydraulic motor that uses direct heat transfer. The working fluid reservoir or container shown in FIG. 28 includes an elongated tube 348. Although the working fluid reservoir may have any desired configuration, can include a large amount of surface area with respect to volume to increase the rate of heat transfer to the working fluid. The embodiment of the working fluid reservoir shown in Figure 28 includes a tube 20 feet long that is 4 inches in diameter, made of "Schedule 80" tube. The tube may include a set 350 for attaching the tube to the conduit to connect the working fluid reservoir to the cylinder. Figure 29 shows an end view of the tube shown in Figure 28, showing a flange 352. The flange 352 may include a plurality of holes 354 for bolts 356 used to connect the flange to another flange for connecting to a conduit for connection to the cylinder. The embodiment of the working fluid reservoir shown in Figures 27 and 28 includes a cooling element 358 inserted inside the tube 348. A cooling fluid can be introduced into the conduit 358 to cool the working fluid. The conduit 358 may be interconnected with the rotation valve 360 to direct the cooling fluid to the relevant working fluid reservoir. In order to absorb high pressures inherent in some working fluids, the cooling fluid conduit 356 is preferably made of a material capable of withstanding the high pressures. According to one embodiment,% inch high pressure steel pipe is used. Although the working fluid pressure may be high, the refrigerant pressure may be low, for example in one embodiment, the refrigerant pressure was from about 32 to about 80 psi. 30 shows a cross section close up of a connection between the working fluid reservoir, the coolant conduit 359, flanges 352 and 353, the gasket 355, and bolts 357. In the embodiment shown in Figure 27, each of the working fluid reservoirs 362, 364, 366, 368 is placed inside a parabolic solar heat collector 370, 372, 374 and 376, respectively. The solar heat collector imparts heat to the working fluid. As the working fluid expands, the cylinders are driven. At the right time, the rotary valve 360 directs refrigerant into each of the working fluid reservoirs. As the coolant is circulated through the working fluid reservoirs, it is heated. The heated coolant is directed to a hot-cold separator 378. To increase imparted to the working fluid by heat solar heat collectors, the present invention may direct heated coolant through the conduit 356. The separator refrigexante cold-heat 378 preferably separates coolant from the working fluid reservoirs that are subjected to expansion from the refrigerant exiting from the working fluid cylinders that are subjected to contraction. The heat can be removed from the refrigerant in the heat exchanger 380. The heat of the refrigerant can be stored in the heat storage device 382. The flow of refrigerant can be controlled by a plurality of pumps. The embodiment shown in Figure 27 includes a coolant pump 384 for directing hydraulic engine coolant from the heat exchanger 380 to rotate the valve 360. The hydraulic motor coolant 384 may be driven by the thermal hydraulic engine. The present invention may further include hydraulic motor heat recycling pump 386. The hydraulic motor heat recycling pump 386 can pump refrigerant from the heat storage device 382 to the rotary valve 360. The heat recycle pump 386 hydraulic motor can also be operated by the thermal hydraulic motor. The embodiment of the thermal hydraulic motor shown in Figure 27 is shown used to drive a hydraulic pump (not shown). The conduits 390 and 392 are for directing hydraulic fluid from the hydraulic pump driven by the thermal hydraulic motor to various loads that are desired to be driven by the thermal hydraulic motor. As indicated above, in the embodiment shown in Figure 27, the hydraulic motor coolant pump 384, the hydraulic motor heat recycle pump 386, and the water pump 388 are driven by the thermal hydraulic motor. Arrows on lines 390 and 392 indicate the direction of hydraulic fluid flow to the loads. The operation of the heat exchanger 380 can be improved by pumping water in the conduits 394 and 396, respectively, into the water pumped by the water pump 388. A thermal hydraulic motor according to the present invention can be formed of any size. For example, from very small motors for use in applications such as biomechanical applications, up to many megawatts power plants can incorporate the thermal hydraulic motor of the present invention. In fact, the thermal hydraulic motor can be designed for use in any application that requires the activation of mechanical energy. A very small motor could include pistons from about 0.5 cm to about 1 cm in diameter. Such a motor could include working fluid reservoirs about the size of a typical body thermometer. In fact, such engines could use heat at approximately the typical temperature of the human body as a source of heat. Refrigeration could be provided by an external evaporative system. A motor of this type could be used in the human body or another body. An example of a use of such a motor is like a heart pump. Another example of an application is for hormone injection. For example, an engine of this type could be used for people with a poor lymphatic system. Such an engine would provide, for example, from about 0.01 horsepower to about 0.1 horsepower. At the other end of the spectrum, very large motors could be formed within the scope of the present invention. For example, an engine that could generate 350 million horsepower would provide approximately 500 megawatts of electric generating capacity. Such a motor could use a piston that has a diameter of approximately 48 inches to approximately 96 inches. The engine could be formed of a heavy-duty steel and reinforced concrete structure. An engine capable of pumping water could generate from about 10, about 50, about 200 horsepower or any between them. Figure 37 shows an embodiment of a water pump of a power horse that drives a thermal hydraulic motor according to the present invention. The heat to expand the working fluid is provided by a solar parabolic heat collector 400; the solar collector preferably includes an actuator 402 for tracking the movement of the sun. The working fluid is supplied to the motor 406. The power produced by the motor 406 is transmitted by the transmission 408 to the pump 409. The invention may include the control 410 for controlling the flow of refrigerant. The motor may further include a battery 412 to provide power. Figure 38 shows an overhead view of the solar heat collectors 400. The motor, shown in Figures 37 and 38, includes direct thermal heat exchange tubes 414. A photovoltaic panel 416 may also be provided to provide electrical power for certain aspects of the invention, such as tracking control and cooling control. Fig. 39 shows an embodiment of a chain drive for seasonal tracking with counterweight that can be used to tilt the solar array to the correct position throughout the year. The embodiment shown in Figure 39 may include a chain drive 600, a motor 602, and a counterweight 604. The motor may be a suitable motor. For example, the engine could be a 12-volt, low-rpm, high-torque engine. Figure 39 also shows the normal position 606 of the solar array. The alignment is articulated around pivot 608. The pivot could be provided by a hinge or other articulatable device. Figure 40 shows an embodiment of a thermal hydraulic motor according to the present invention that uses electric heat as a source to impart heat to the working fluid. The embodiment shown in Figure 40 includes four radially disposed cylinders. Figure 40 also shows a gear that can be used to multiply the power produced by the engine. The embodiment shown in Figure 40 includes work fluid reservoirs 720 comprising a tube 4 inches in diameter, 24 inches long. The coolant circulates through the working fluid in line 700 of% inch. The heat is provided by an electrical resistor 718 that can use 120 V AC power. Coolant fluid reservoirs can be closed by a 2-inch welded neck flange 724. The pistons 702, 704, 706 and 708 included in the cylinders 710, 712, 714 and 716 in the embodiment shown in Figure 40 are two inches in diameter and 8 inches in length. The outside diameter of the pistons 702, 704, 706 and 708 is 4 inches. The cylinders are arranged radially as in the embodiment shown in Fig. 27. Fig. 40 also illustrates a plurality of gears and connecting strings or chains, collectively identified as 722, which can be used to multiply the power generated by the thermal hydraulic motor. Figure 41 shows an alternative view of the engine shown in Figure 40. Figure 43 illustrates an embodiment of a thermal hydraulic motor according to the present invention that includes a passive solar collector 900. The flexible pipes 902 and 904 connect the solar collector to a 906 double action cylinder. The motor is used to pump water from a well. Figure 44 illustrates and depicts a further embodiment of a cylinder, piston and crankshaft arm according to the present invention. The above description of the invention illustrates and describes the present invention. Additionally, the description shows and describes only the preferred embodiments of the invention, but as mentioned above, it is to be understood that the invention is capable of use in various other combinations, modifications and environments and is capable of changes or modifications within the scope of the invention. scope of the invention concept, as expressed herein, in accordance with the above teachings, and / or the experience or knowledge of the pertinent art. The embodiments described above are intended to explain the best known ways of practicing the invention and enable other skilled in the art to use the invention in such, or other, embodiments and with the various modifications required by the particular applications or uses of the invention. Accordingly, the description is not intended to limit the invention to the form described herein. In addition, it is intended that the appended claims be construed to include alternative embodiments.

Claims (22)

1. A thermal hydraulic motor, comprising: a frame; a working fluid that changes the volume as the temperature changes; a reservoir of working fluid for housing said working fluid; a cylinder secured to said frame and including an interior space, said cylinder also including a step for introducing said working fluid into said interior space; a piston housed inside said interior space of the cylinder, said working fluid reservoir defining said interior space of said cylinder, said piston, and said working fluid reservoir a closed space filled by said working fluid; and means for transmitting and removing heat from said working fluid, thereby alternately causing said working fluid to expand and contract without subjecting it to a phase change, said piston moving in response to said expansion and contraction of said fluid. of work.

2. A heat engine according to claim 1, further comprising: a transfer section of the working fluid between said reservoir of the working fluid and said interior space of said cylinder, said reservoir of the working fluid defining said connection of working fluid, said inner space of said cylinder and said piston a closed space filled by said working fluid.

3. A thermal hydraulic motor according to claim 1, further comprising: a plurality of cylinders, pistons, working fluid reservoirs, and heat transfer means.

A thermal hydraulic motor according to claim 1, further comprising means for mounting said cylinder in said frame, said mounting means allowing said cylinder to slide and articulate relative to said frame, said mounting means including connecting rod provided on the cylinder, said connection rod being hingedly secured to said member slidably mounted on said frame, said sliding member sliding in a direction perpendicular to said crankshaft.

A thermal hydraulic motor according to claim 1, wherein said means for transmitting and removing heat from said working fluid is at least one heat exchanger.

6. A thermal hydraulic motor according to claim 5, further comprising a water jacket surrounding said working fluid reservoir, said water jacket including an inlet and outlet for water of different temperatures to impart or remove heat from said working fluid through said heat exchanger.

7. A thermal hydraulic motor according to claim 1, wherein there are no valves that restrict the movement of said working fluid as it expands.

8. A thermal hydraulic motor according to claim 1, further comprising: a connecting rod fixed to said piston; a crankshaft fixed to said connecting rod; and a camshaft, where the movement of said camshaft is controlled by said crankshaft and controls the opening and closing of said valves or the opening and closing of micro-switches that activate solenoid valves.

9. A thermal hydraulic motor according to claim 8, wherein said connecting rod is hingedly fixed to said piston.

A thermal hydraulic motor according to claim 8, wherein said connecting rod is fixed immovably to said piston and said cylinder is mounted in an articulated manner on said frame.

11. A thermal hydraulic motor according to claim 8, further comprising: transmission means for increasing or increasing the speed of the crankshaft.

12. A thermal hydraulic motor according to claim 8, further comprising: at least one seal between an outer surface of said piston and an inner surface of said inner space of the cylinder.

13. A thermal hydraulic motor according to claim 1, wherein said working fluid has a high temperature water between about 120 ° and about 140 ° F, and said working fluid has a water at a low temperature between about 70 ° and about 85 ° F.

A thermal hydraulic motor according to claim 1, wherein said working fluid has a high temperature between about 80 ° and about 200 ° F, and said working fluid has a water at a low temperature between about 35 ° and about 140 ° C. F.

15. A thermal hydraulic motor according to claim 1, wherein a temperature differential between a high temperature of said working fluid and a low temperature of said working fluid is sufficient to provide a minimum expansion required to move said piston to through a complete cycle.

16. A thermal hydraulic motor according to claim 1, further comprising: two connecting rods attached to opposite sides of said piston; and two crankshaft shafts, one fixed to each of said connecting rods.

17. A thermal hydraulic motor according to claim 1, wherein said piston and said interior space of said cylinder define two closed spaces filled by said working fluid, further including said cylinder: a main inlet in the vicinity of said cylinder. a first end of said cylinder; 'a secondary inlet in the vicinity of a second end of said cylinder; and means for sealing a space between said cylinder and said connecting rod; said thermal hydraulic motor including at least one joint between an outer surface of said piston and an inner surface of said inner cylinder space; wherein the expansion of said working fluid is used to reciprocate said piston in opposite directions.

18. A thermal hydraulic motor according to claim 1, wherein said working fluid is pressurized.

19. A thermal hydraulic motor according to claim 1, further comprising means for mounting said cylinder in said frame, said mounting means allowing said cylinder to slide and articulate relative to said frame, said mounting means including a rod. connection provided on said cylinder, said connection rod being hingedly secured to a member slidably mounted to said frame, said slidable member sliding in a direction parallel to said cylinder.

20. A thermal hydraulic motor according to claim 1, further comprising at least one spring biasing said piston to move in a direction opposite to a direction in which expansion of said working fluid causes said piston to move.

21. A thermal hydraulic motor according to claim 3, wherein said cylinders are arranged radially.

22. A thermal hydraulic motor, comprising: a frame; a first working fluid that changes the volume as the temperature changes; a reservoir of working fluid for housing said first working fluid; a flexible diaphragm provided at one end of said working fluid reservoir, said flexible diaphragm moving in response to the expansion and contraction of said working fluid; a reservoir for housing a second working fluid in contact with said flexible diaphragm; means for transmitting and removing heat from said working fluid, thereby alternately causing the working fluid to expand and contract, causing the expansion and contraction of said first working fluid to move said flexible diaphragm, causing the movement of said flexible diaphragm the movement of said second working fluid; a cylinder secured to said frame and including an interior space, said cylinder also including a step for introducing said second working fluid into said interior space; a piston housed inside said interior space of said cylinder, said reservoir of the working fluid, said interior space of said cylinder, and said piston defining a closed space filled by said second working fluid.