Title of Invention

"THERMAL HYDRAULIC ENGINE"

Abstract

A thermal hydraulic engine including a frame. A working fluid changes volume with changes in temperature. A working fluid container houses the working fluid. A cylinder secured to the frame includes an interior space. The cylinder also includes a passage for introducing the working fluid into the interior space. A piston is housed within the interior space of the cylinder. The working fluid container, the interior space of the cylinder, the piston, and the working fluid container define a closed space filled by the working fluid. The engine also includes means 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 moves in response to the expansion and contraction of the working fluid.

Full Text

THERMAL HYDRAULIC ENGINE Field of the Invention The invention relates to an engine that is powered by the expansion and contraction of a working fluid as heat is alternately applied to and removed from the working fluid. Background of the Invention Typically, energy is not in readily utilizable forms. Many means exist for converting one type of energy to another. For example, an internal combustion engine can turn the explosive force of a fuel burned in its cylinders into mechanical energy that eventually turns the wheels of a vehicle to propel a vehicle. An internal combustion engine channels energy resulting from the burning of a fuel in a cylinder into a piston. Without the cylinder and piston, the energy resulting from the burning of the gas would simply spread out in every 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 moving air into electricity. While an internal combustion engine typically produces mechanical energy from the burning of fossil fuels, such as gasoline, diesel fuel, or natural gas or alcohols, other attempts have been made to produce mechanical energy from the movement of members such as pistons by means other than the burning of fossils fuels. However, most of these devices still operate on the basic principle of providing a force to drive a moveable member such as a piston. The difference among the various devices in the way in which the force is produced to move the piston and the way in which the force is controlled. Some of these devices utilize the movement of a working fluid to drive a moveable member, such as a piston. Other devices utilize the phase change in a liquid to drive a moveable member. In their operation, some devices utilize valves to control the flow of a working fluid in the production of mechanical energy by moving a moveable member. Due to the worldwide and ever increasing demand, research constantly focuses on ways to produce energy or power the devices that we rely on in our daily lives. In recent years, another area of research has included alternative sources of energy. Such research has constantly increased. Among the reasons for the increased research is an increased awareness of the limited amount of fossil fuels in the earth. This research may also be spawned by an increased desire to provide energy for people living in remote locations around the world who now live without power. Among the alternative sources of energy on which research has been 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 sun's heat for use in a variety of ways. As discussed above, in relation to the internal combustion engines and windmill examples, the problem being addressed both by photovoltaic solar cells and solar heating devices is the conversion of one type of energy to another type of energy. In solar cells, the energy in sunlight is used to excite electrons in the solar cells, thereby converting the sun's energy to electrical energy. On the other hand, in solar heating cells, the energy of the sun is typically captured by a fluid, such as solar hot water panels typically seen on, the rooftops of residences. Summary of the Invention The present invention was developed with the above described problems in mind. As a. result, the present invention is directed to a new device for converting one form of energy to another. The present invention may also utilize solar or other unconventional forms and/or sources of energy. Accordingly, the present invention provides a thermal hydraulic enqine that utilizes the expansion and contraction of a fluid by alternately transmitting heat to and removing heat from an operating fluid. The energy may provide mechanical and/or electrical energy. One advantage of the present invention is that it may utilize a variety of sources of heat to heat and/or cool the working fluid. Consequently, another advantage of the present invention is that it is substantially non-polluting. Along these lines, an additional advantage of the present invention is that it may run off heat energy and, therefore, may be solar powered. Furthermore, an advantage of the present invention is that, since it may be solar powered, it may be utilized to provide power in remote areas. An additional advantage of the present invention is that it may utilize heat and/or heated water produced by existing processes. Accordingly, the present invention may make use of heat energy that is otherwise currently not utilized and discarded as waste. A still further advantage of the present invention is that it may operate without using fossil fuels. It follows"that an advantage of the present invention is that it may produce energy without contributing to the abundance of waste gases and particles emitted into the atmosphere by the burning of fossil fuels. Also, an advantage of the present invention is that it may 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, thus reducing construction and maintenance costs. In accordance with these and other objectives and advantages, the present invention provides a thermal hydraulic engine. The engine includes a frame. The engine utilizes a working fluid that changes volume with changes in temperature. A working fluid container houses the working fluid. A cylinder is secured to the frame and includes an interior space. The cylinder also includes a passage for introducing the working fluid into the interior space. A piston is housed with the interior space of the cylinder. The working fluid container, the interior space of the cylinder, the piston, and the working fluid container define a closed space filled by the working fluid. The engine also includes means 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 moves in response to the expansion and contraction of the working fluid. According to additional preferred aspects, the present invention provides a thermal hydraulic engine. The engine includes a frame. The engine also includes a working fluid that changes volume with changes in temperature. A working fluid container houses the working fluid. A flexible diaphragm is provided at one end of the working fluid container. The flexible diaphragm moves in response to 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 movement of the flexible diaphragm. The engine also includes means for transmitting heat to 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 become readily apparent by those skilled in the art from the following detailed description, wherein it is shown and described only the preferred embodiments of the invention, simply by way of illustration of the best mode contemplated of carrying out the invention._ As will be realized, the invention is capable of other and different embodiments, and its several details are capable of modifications in various obvious respects, without departing from the invention. Accordingly, the drawings and description are to be regarded as illustrative in nature and not as restrictive. Brief Description of the Drawings Figure 1 represents a schematic diagram illustrating an embodiment of a power plant including a thermal hydraulic engine according to the present invention; Figure 2 represents a schematic diagram illustrating various components of an embodiment of a solar powered thermal hydraulic engine according to the present invention; Figure 3 represents an overhead view of various components that may be driven by a thermal hydraulic engine according to the present invention, representing the "load" on the engine; Figure 3a represents an embodiment of a chain drive gear and sprocket that may be driven by a thermal hydraulic engine according to the present invention; Figure 4 represents a schematic diagram illustrating various components of another embodiment of a solar powered thermal hydraulic engine according to the present invention utilized to drive a water pump; Figure 5 represents an embodiment of a thermal hydraulic engine according to the present invention including three cylinders; Figure 6 represents the various stages of the operation of an embodiment of a thermal hydraulic engine according to the present invention that includes three cylinders; Figure 7 represents an embodiment and operation of a thermal hydraulic engine according to the present invention that includes four cylinders; Figure 8 represents the position of a piston at the beginning of a power stroke of a piston of an embodiment of a thermal hydraulic engine according to the invention; Figure 9 represents the rotational location of a crank shaft in a thermal hydraulic engine according to the present invention, indicating the various positions of the crank shaft relative to the expansion and contraction of the working fluid and introduction and removal of heat from the working fluid; Figure 10 represents a graph showing operating ranges of temperatures and pressures of a working fluid utilized in an embodiment of a thermal hydraulic engine according to the present invention; Figure 11 represents a cross-sectional view of an embodiment of a heat exchanger for use with a thermal hydraulic engine according to the present invention; Figure 12 represents a cross-sectional view of an embodiment of a heat exchanger and working fluid container for use with a thermal hydraulic engine according to the present invention that employs mercury as a working fluid; Figure 13 represents an embodiment of a containment wall for use with an embodiment of a working fluid container according to an embodiment of the present invention; Figure 14 represents a cross-sectional view of another embodiment of a cylinder and piston that may be employed in a thermal hydraulic engine according to the present invention; Figure 14a represents a cross-sectional view of the embodiment of a piston and connecting rod shown in Figure 14; Figure 15 represents a close-up cross-sectional view of a portion of the embodiment of a cylinder and piston shown in 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 engine according to the present invention that includes a flexible flange for transmitting the force generated by an expansion of the working fluid to a hydraulic fluid and, ultimately, to a piston. Figure 17 represents a side view of an embodiment of a thermal hydraulic engine according to the present invention that includes a cylinder mounted to a crankshaft and pivotably mounted to a floating anchor sliding within a guide mounted to a frame; Figure 18 represents the embodiment shown in Figure 17, wherein the piston is starting its power stroke and the crankshaft has started to rotate; Figure 19 represents the embodiment shown in Figures 17 and 18, wherein the piston has started its return stroke and the floating anchor is sliding back into its guide; Figure 20 represents a side view of an embodiment of a thermal hydraulic engine according to the present invention that includes two springs for biasing the piston in the direction of its return stroke and a floating anchor shown in Figures 17-19; Figure 21 represents a side view of an embodiment of a thermal hydraulic engine according to the present invention that includes a frame that components of the engine are mounted on; Figure 22 represents a cross-sectional view of an embodiment of a cylinder of a thermal hydraulic engine according to the present invention in which a heat exchanger is mounted within the working fluid container; Figs. 23A-23H represent cross-sectional views of an embodiment of a thermal hydraulic engine according to the present invention that includes four cylinders radially arranged, illustrating the engine throughout various portions of a cycle of the engine; Fig. 24 represents a perspective view of the embodiment shown in Figs. 23A-23H; Fig. 25A represents an embodiment of a cylinder that may be included in a thermal hydraulic engine according to the present invention wherein the cylinder includes a single inlet and outlet port for passage of a working fluid into and out of the cylinder; Fig. 26 represents an embodiment of a cylinder that may be included in a thermal hydraulic engine according to the present invention wherein the cylinder includes two ports for passage of hydraulic fluid into and out of the cylinder, such that the return stroke of the piston is also a powered stroke; Fig. 27 represents a schematic view of an embodiment of a thermal hydraulic engine according to the present invention that includes direct thermal exchangers rather than heat exchangers for introducing heat into the working fluid of the thermal hydraulic engine; Fig. 28 represents a cross-sectional view of an embodiment of a direct thermal exchanger that may be utilized in an embodiment of the invention shown in Fig. 26; Fig. 29 represents an end view of the direct thermal exchanger shown in Fig. 28; Fig. 30 represents a close-up end view of the direct thermal exchanger shown in Figs. 28 and 29; Fig. 31 represents a cross-sectional view of an embodiment of a mechanical valve that may be utilized to direct working fluid and/or heating fluid and/or cooling fluid to various parts of a thermal hydraulic engine according to the present invention; Fig. 32 represents a cross-sectional view of an embodiment of a crankshaft and a piston crank arm that may be included in a thermal hydraulic engine according to the present invention; Fig. 33 represents a cross-sectional view of the crankshaft shown in Fig. 32 showing multiple positions of the piston crank arm throughout a portion of the cycle of the engine; Fig. 34 represents a cross-sectional view of a cylinder of a thermal hydraulic engine according to one embodiment of the present invention that includes a crankshaft shown in Fig. 31 - Fig. 33, illustrating the position of the piston crank arm throughout a portion of the cycle of the engine; Fig. 35 shows a cross-sectional view of another embodiment of a crankshaft and piston crank arm arrangement that may be utilized in a thermal hydraulic engine according to the present invention; Fig. 36 represents a side view of a crank moment arm that includes stiffening ribs; Fig. 37 represents another embodiment of a thermal hydraulic engine according to the present invention and various associated components including a solar heat collector; Fig. 38 represents an overhead view of the solar heat collector shown in Fig. 37; Fig. 39 represents a cross-sectional side view of a solar heat collector according to the present invention including a seasonal tracking chain drive and counterweight showing various positions of the solar heat collector; Fig. 40 represents a further alternative embodiment of a thermal hydraulic engine according to the present invention; Fig. 41 represents a still further alternative embodiment of a thermal hydraulic engine according to the present invention; Fig. 42 represents an embodiment of a transmission that includes a flywheel that may be used with an embodiment of a thermal hydraulic engine according to the present invention; Fig. 43 represents an embodiment of a thermal hydraulic engine according to the present invention that includes a piston that is powered both on its power stroke and its return stroke, includes a passive solar heat collector as a heat source, and powers a water pump; and Fig. 44 represents a further embodiment of a cylinder, piston and crank arm according to the present invention. Detailed Description of Various and Preferred Embodiments of the Invention As stated above, the present invention is an engine that derives power from the expansion and contraction of a working fluid as heat is alternately applied to and removed from the working fluid. The expansion and contraction of the fluid is transformed into mechanical energy, via the present invention. The mechanical energy may be utilized directly. Alternatively, the mechanical engine may be turned into another form of energy, such as electricity. Accordingly, the present invention includes a working fluid that experiences changes in volume with changes in temperature. Any such fluid may be utilized in a thermal hydraulic engine according to the present invention. However, more power may be realized from the operation of the engine if the working fluid experiences greater changes in volume over a range of temperatures than fluids that experience lesser changes in volume over the same temperature range. The present invention operates at least in part on the principle that fluids are generally not compressible. Therefore, according to the present invention, the working fluid does not change form into another state, such as a solid or a gas during the operation of the engine. However, any fluid that undergoes an expansion or contraction with a change in temperature may be utilized according to the present invention. Among the characteristics that may be considered in selecting a working fluid are the coefficient of expansion of the working fluid and the speed at which heat is transferred to the fluid. For example, if a fluid quickly changes temperature, the speed, of the engine may be faster. However, in some cases, a fluid that quickly responds to changes in temperature may have a low coefficient of expansion. Therefore, these factors must balanced in order to achieve the desired effect for the engine. Other factors that may be considered in selecting a working fluid include any caustic effects that the fluid may have on the working fluid container, the environment, and/or people working with the engine. A very important factor in determining the size, design, cost, speed, and other characteristics of a thermal hydraulic engine according to the present invention is the working fluid. Various fluids have various thermal conductivities and coefficients of expansion, among other characteristics, that may effect the characteristics of the engine. For example, the coefficients of expansion of the working fluid may determine the amount of working fluid necessary to operate the engine. The coefficient of expansion may also effect the amount of heat necessary to expand the working fluid. Changing the amount of heat necessary to expand the working fluid may change the size of a solar heat collector providing heat, the size of a heat exchanger imparting heat, among other factors. In embodiments of the present invention in which heat is provided by other sources of energy, the amount of energy necessary to generate heat to expand the working fluid may be altered based upon the thermal expansion characteristics. For example, if a fluid expands to a high degree as heat is imparted to it, less heat will be required to provide the necessary expansion for the engine. This permits a decrease in the size of solar collectors, a decrease in the amount of energy necessary 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 engine that includes a solar heat source. Although the embodiment shown in Fig. 27 includes solar heat collectors, a variety of heat sources may be utilized, whether the direct heat transfer or heat exchangers are utilized. For example, a thermal hydraulic engine according to the present invention may utilize low grade heat to perform work. A thermal hydraulic engine according to the present invention may also utilize medium and high grade sources for fuel. Examples of fuel sources that may be utilized include natural gas, hydrogen gas, liquified petroleum gases, gasoline, fuel oils, coal, nuclear, or other fuels. One skilled in the art would know how to devise a system to impart heat to the working fluid of the present invention when utilizing any of the above-discussed fuels. An example of a working fluid that may be utilized according to the present invention is water. Another fluid that may be utilized is mercury. Additionally, other substances that may be utilized as a working fluid include FREON, synthetic FREONS, FREON R12, FREON R23, and liquified gasses, such as liquid argon, liquid nitrogen, liquid oxygen, for example. FREON and related substances, such as synthetic FREONS, FREON R12, and FREON R23, may be particularly useful as a working fluid due to the large degree of expansion that they may undergo as heat is introduced into them and the tendency to return to their original volume and temperature upon removal of heat. Another example of a working fluid that may be utilized according to the present invention is liquid carbon dioxide. Other fluids that may be utilized as working fluids include ethane, ethylene, liquid hydrogen, liquid oxygen, liquid helium, liquified natural gas, and other liquified gases. Other working fluids may also be used, as one skilled in the art could determine without undue experimentation once aware of this disclosure. In order to capture the energy in the expansion of the fluid, the working fluid is housed within a closed space. The closed space may include many different elements. However, the closed space typically includes at least a working fluid container. Preferably, the working fluid entirely fills or substantially entirely fills the interior of the working fluid container when the working fluid is in a non-expanded or substantially non-expanded state. In other words, typically, the working fluid is placed in the working fluid container at its densest state, wherein it occupies the least amount of volume. The working fluid container may then be sealed or connected to other components of the engine. The volume of the working fluid container depends upon, among other factors, the size of the engine, the application, the amount of working fluid required for the application, the amount that the working fluid expands and contracts with changes in temperature. The exact interior volume of the working fluid container will be discussed below in relation to specific embodiments. However, such embodiments are only illustrative in nature and not exhaustive and, therefore, only represent examples of working fluid containers. Preferably, the working fluid container is made of a material that can withstand the pressure from the working fluid as the working fluid expands. Materials that may be utilized to form the working fluid container include metals, such as copper, plastics, ceramics, carbon steel, stainless steel or any other suitable materials that may withstand the temperatures and pressures involved in the specific application. Regardless of the material used, preferably, it is non-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 preferably not due to the force from the expanding fluid. The non-deformability of the material that working fluid container is made is helpful for transmitting the force of the expansion of the working fluid to whatever moveabie member, such as a piston, the particular embodiment of the present invention includes. Another stress that the working fluid container is subjected to results from the heating and cooling of the working fluid. As the temperature of the working fluid increases, the working fluid container may expand, due to the application of heat. Similarly, as the working fluid cools, the materials in contact with the fluid will cool and may contract. Therefore, regardless of the material used, not only should it be capable of withstanding temperatures and pressures of a particular application, but it must also be able to withstand the changes in temperatures and pressures that continuously occur during the operation of a thermal hydraulic engine according to the present invention. For instance, metal fatigue could be a problem in embodiments in which are made of metal. However, metal fatigue may be overcome 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 container, also have some elastic characteristics. A material that is excessively brittle might tend to crack and leak, rendering the engine inoperable. The number of working fluid containers included an embodiment of the present invention typically depends upon the number of cylinders or other devices utilized for capturing the energy of the expansion of the working fluid. Preferably, the number of working fluid containers is equal to the number of expansion capturing devices. However, it. conceivable that there could be more or less working fluid containers. For example, one embodiment of the present invention includes a piston that is moved back and forth within a cylinder in both directions by the expansion of the working fluid. Such an embodiment may include two working fluid containers for each cylinder. Therefore, as can be appreciated, the number of working fluid containers in the embodiment of the invention may vary. The working fluid container may be interconnected with a cylinder. Alternatively, the working fluid container may be isolated in a fluid containment system. According to such a system, the force generated by the expansion of the working fluid is not transmitted directly to a piston or other movable member, but is indirectly transmitted. If the working fluid container and cylinder are connected so that the force of the expansion of the working fluid is directly transmitted to a piston or other movable member, the working fluid container and cylinder may be interconnected in a variety of ways. For example, a tube, hose or other conduit may be utilized to connect the working fluid container with the cylinder. Alternatively, the working fluid container may be directly connected to the cylinder. Preferably, if the cylinder is connected to the working fluid container with a hose or other conduit, the hose or conduit is also made of a material the resists changes in shape as a result of the forces applied by the expansion of the working fluid. An example of such a material includes steel reinforced rubber hose. As stated above, the working fluid may be isolated in the working fluid container. According to such embodiments, rather than being directly transmitted to the piston, the force of the expanding fluid may be transmitted to a hydraulic fluid, which then transmits the force to the piston. According to such embodiments, the working fluid is housed within the working fluid container. The working fluid container is in contact with the heat exchanger. However, rather than the working fluid traveling from the working fluid container into a cylinder to actuate a piston as the fluid expands, the end of the working fluid container that is not surrounded by the heat exchanger is closed a flexible blind flange. In the embodiment shown in Figure 12, the working fluid container and the hydraulic system may be thought as defining two sections making up an overall fluid containment system. The flexible blind flange 180 may be thought of as isolating the working fluid. Therefore, the working fluid container 182 in such embodiments may be referred to as a fluid isolation section. Another part of Lhe fluid containment system is the hydrauiic system 184. The hydraulic system may be thought of as a transfer sestion that transfors the fores of the working fluid to the pision, a fluid coneainrcent system is pasViculariy useful if: the working fluid is a caasti- or hazardous material, such as mercury. Woe only does the containment a ad transfer -section psrrr.it a hazardous working fluic. to be usad with the engine cat is alsc camits the sections of the ergine to be manufactured separate iv and separately. Fnr the working fluid with or exchanger 136, coula irotn the neat exchanger s.nd cylinder tc which it is be i nt erconrected wich . The fluid containment system includes the flexible blind flange as well as the hydraulic reservoir and other hoses, fittings, tubing, And passageways thac necessary to permit the hydraulic fluid to operate the pi hydraulic tluid. Regardless of the components and materials utilized in ccn. fluid contair.Tr'sr.t system, preferably it maintains the temperature and pressure of the working fluid. According to one such ephodir.Mounting flai.ga 133 extends about the opting of the fluid container 182. Preferably, the flexible blind flange ISO is then positioned on The mounting flange 13S connected to the wording fluid container 182. Th hydraulic fluid rervoir may then be attaThed ever the flexible blind flange. Preferably, the hydraulic ilud reservoir preferably includes a mount ig flange 190 having shape corresponding tc the snape of The mounting flange 1.38 on the working fluid container 182. The hydraulic fluid reservoir and the working fluid container may Then be ui.g:r::y connected together in order =0 31 The space betwen thn,,. tbsrejy prenting the working fluid from The hydrsulic; fluid reservoir, is connected directly or through one or more conduits to the cy'Uid.sr.. liaia thrtii actg as tfre wrkirg fluid ether wie would if it were not .isolacad in the working fluid container. According tc such an ra&od. tfi working fluid axpArxdP, if. applies nrecfflvrn th flexilli blind ioye. Tne flexible bli.d flange then appli&s force to the hydraulic fluid, A, pressure is ter. created en the hydraulic fluid, The pressure applied to the hydraulic fluid, causes it to plac pressure on all surface of the reservoir, cylinder, and piston, pit the piston is only movable member in system, it moves in response to pressure. Figare 13 shews containment wail between . interior of the wording fluid container and interior of: heat number of working fluid containers and possibly cont&in.'.Snt sections may vary, depending upon, amorg o factors, number of cylinders and wher a power return stroke, as described below, is utilized. As discussea above, working fluid expands and, eir or indirectly, expanding fluid is directed to a cylinder. cylinder its at heart of invention since cylinder nouses piston that force of expanding working is transmitted to, reby moving cylinder and nical energy produced by invention. As with working fluid container and or components of invention, cylinder may be made of a variety of materials. above discussion regarding stresses on working fluid oaiuei and material that it is made of applies to l;he cylinder. Accordingly, same materials may be utilisd. to form cylinder. size vf cylinder may vary, depending upon a nujiber of factors related to specific application. Factors that may be important is determining size of cylinder irduda, amciig oThers, number of cylinders, r.he particul.'ii load on 'The engine, and amount of ver to js pi'cciucec.. A typijiil size of maxinrun, intfi.ricr 'vxAns of a cylinder included i.ri a rmal hydraulic engine according to The present irvsntlon is from about 350 cui;ic inThes to about 20,000 cubic iu:hea. However., size of acn of cylinders may vary from ajsout 4 inThes in dis.istar to about 3 inThes in diameter. According to erv ifricdiir,ent , an engine with a cylinder having a viiawecer ot about 5 inThes and a piston stroke cf ai;out 18 inThes generates about 10 horsepower, Preferably, cylinder has a circular or substantially circular cross Eecticrai shape. figures 5. 7, and 14 illustrate exaaiplesi of various embodiments of cyli.ndfi.rs that may be utilised in a rmal hydraulic arigiina .according to present invention. Tiie cylinder may be mounted to a. frams upon which or component..? of present invention ruiy be mounted. cylinder may ba fi:calsly or articulately mounted to frame yigurea 17, is, and "19 ,ihcw an embodiment of present invention in which Thes oyi indcr 20 is articulately or pivotabiy mounted to a frame 202. According to this embodiment, cylinder 200 includes a connecting member 204, such as a fork or or suitable member, that may be pivotabiy joined to a complementary member on frame 202. A pin 205 rcaar.ja for connecting cylinder tc Sraie thai: may be uciiized. . As piston moves through its cycle, and crankshaft rotates, t.hs cylinder will pivot about its anrhor. embodiment shown in Figuras also includes a floating anchor. According to this szribod.P'S.nt, cylinder is pivotabiy [aount&d to anchor to that cylinder can pivot. Trie anchor is movably mounted within a guide 208. guide 208 permit anchor to slide from right to left as shown i" Figures 17. Tne guide 208 may be directly or indirectly connected to frame 202. floaci. anchor permits piston to contract without having to wait tor crankshaft to continue its rotation and without, having to overcome any or forces tending acting or. piston in a direction opposite to its return stroke. Regardless of embodiment of present invention, it may include a floating anchor. Figura 20 shews an embodiment of a rmal hydraulic engine according to present invention that includes spring.1? 210 that bias or tend to move piston in direction of its return stroke. If engine includes springs, it may include at least one spring. Use of springs to cause cylinder to move in direction of its return stroke may be important to maintain a pressure on working fluid at all times. With some working fluids, this is particularly important, such as with FREON, FREON substitutes and analogous compounds. According to embodiments shown in Figures 5, 6, and 7, working fluid is introduced into one end of cylinder. refore, cylinders according to se embodiments include a connection only at this end. However, according to or embodiments, discussed below in greater detail, return stroke, as well as power stroke, is powered by a working fluid. According to such embodiments, cylinder may include means for introducing a working fluid into both ends of cylinder. Such embodiments may also include a seal about a connecting rod attaThed to piston, as described below in greater detail. working cylinders of a rmal hydraulic engine according to present invention may include a port for passage of working fluid into and out of cylinder. According to such embodiments, expansion of working fluid powers piston through its power stroke. Such an embodiment is shown in crosssection in Fig. 25. In this embodiment, cylinder 326 includes an inlet 328 for introduction of working fluid into cylinder. Expansion of working fluid applies force to wall of surface area that defines space 330 into which working fluid is introduced. As working fluid expands, it applies force to face 332 of piston 334 located within cylinder 326. Seal 336 prevents fluid from entering remaining portion of interior volume of cylinder. Force applied to surface of piston moves piston into an extended position, as shown by 338. piston may be powered on its return stroke by forces created by contraction of fluid, as well as by forces applied to crank arm 340 by or cylinders in a multicylinder engine as y experience ir power stroke or by or forces. Fig. 26 shows an alternative embodiment of a cylinder according to present invention that includes two ports 344 and 346 for passage of a working fluid into and out of cylinder. Including two ports for passage of a working fluid into and out of ' cylinder permits piston to be powered in both directions of movement. In or words, piston constantly experiences a power stroke regardless of direction of movement of piston. Such an embodiment does not require outside forces to cause cylinder to return. A dual port cylinder also permits one piston to do work in two directions. Significantly, a dual port cylinder may permit a rmal hydraulic engine according to present invention to operate with only one cylinder. Anor benefit of including dual port hydraulic cylinders in a rmal hydraulic engine according to present invention is that size of engine may be decreased since cylinder may provide power to operate a load with cylinders moving in each direction. Although engine may be reduced in size, a single cylinder with two ports cannot replace two cylinders with a single port since port on side of piston where piston shaft is mounted applies less force to piston since surface area of piston is reduced by area of shaft. An additional added benefit of dual port hydraulic cylinders is that flow of working fluid between cylinders may be interconnected. According to such an embodiment, main port, which would be port that fluid flows into to drive piston in its power stroke in a cylinder that includes only one port, such as port 344 in embodiment shown in Fig. 26, may be connected to a second port, such as port 346 in embodiment shown in Fig. 26 of a different cylinder. An embodiment that includes interconnected cylinders permits a piston to be pushed by a first cylinder being powered by fluid flowing into main port and pulled by fluid exiting second port on that cylinder. According to such an embodiment, crankshaft will constantly be rotated by force applied by all cylinders as pistons are constantly being moved by working fluid flowing into and out of first and second ports simultaneously. Such a design permits size of engine to be decreased. According to one embodiment, a rmal hydraulic engine including two ports per cylinder may be decreased by almost onehalf size, compared to an engine that includes single port cylinders. effect of a dual port cylinder may be at least partially achieved utilizing a single port cylinder if a gas is provided on side of piston opposite working fluid. gas may be pressurized to maintain equilibrium of pressures on piston when piston is in a fully withdrawn position. As piston moves on its power stroke, gas will be compressed as working fluid pushes against piston. greater hydraulic force of working fluid will typically be much greater than pneumatic force provided by gas. refore, gas typically will only slightly restrict forward motion of piston. As working fluid contracts, hydraulic forces on piston are reduced. reduced hydraulic forces typically are close in magnitude to pneumatic forces generated by gas, reby permitting gas to help piston return to starting position. design of a chamber, utilizing a gas as described above as a spring, maybe designed to avoid developing extreme pressures. gas pressure should be higher than hydraulic pressure at equilibrium position. Additionally, gas pressure should be great enough to overcome inertia of piston and frictional forces of 0ring seal between piston and cylinder wall. As stated above, a rmal hydraulic engine according to present invention may include only one cylinder. single cylinder may be power by fluid flowing into and out of two ports included in vicinity of opposite ends of cylinder. A single cylinder from a hydraulic engine according to present invention may also include at least one flywheel attaThed to transmission system to permit full rotation of a crankshaft. Fig. 42 shows an embodiment of a transmission that may be utilized with a rmal hydraulic engine according to present invention. transmission shown in Fig. 42 includes a plurality of gears 800 to gear up power created by engine. flywheel 802 is on higher RPM side of gear up of transmission. center shaft 804 is main crankshaft of engine, typically operating at a low rate of revolution. gears are mounted on 6 inch by 0.5 inch steel plates 806. Also, in embodiment shown in Fig. 42, gears are mounted about 16 inThes apart. Of course, one skilled in art could utilize a different number of gears mounted in a different manner on different supports. One skilled in art could also connect gears toger and to engine in a different manner. Actually, oretically, a rmal hydraulic engine according to present invention could include a single cylinder that only includes a single port for introduction of a working fluid if a flywheel of a size sufficient to permit rotation of crankshaft is provided. One skilled in art could determine size of flywheel necessary without undue experimentation based upon disclosure contained herein. A displacable member piston may be located within cylinder. One example of such a displacable member is a piston. displacable member will slide back and forth along length of cylinder in response to changes in volume of fluid with changes in temperature. In order to maintain working fluid in a closed space, preferably, working fluid is prevented from passing between cylinder and piston. This may be accomplished by providing a piston having a crosssectional area only very slightly less than crosssectional area. Also, helping to ensure a seal between piston and cylinder is if piston has substantially same cross sectional shape as ross sectional shape of interior of cylinder. Any space between piston and cylinder may be furr sealed by providing a seal about piston. Alternatively, a seal may be located on surface of piston facing interior of cylinder about edge of piston. seal helps to ensure that space between piston and cylinder is sealed. Sealing space helps to ensure that any energy that may be derived from expansion of fluid will be transferred to piston and not be wasted by fluid leaking between piston and cylinder. If fluid were to leak, it could greatly degrade performance of engine. Figures 14, 14a, and 15 show an alternative embodiment of a piston and cylinder arrangement that may be utilized in an engine according to present invention. According to this invention, working fluid is introduced into cylinder on both sides of piston 192. Accordingly, area where piston and cylinder wall 194 meet is sealed by seals 196 and 198 on both sides of piston 192. In order to transmit force from piston to a crankshaft or or transmission member, a connecting rod may be attaThed to piston. In embodiments without a powered return stroke, connecting rod may be connected to side of piston opposite side facing working fluid, or hydraulic fluid in embodiments including a working fluid containment system. In embodiments including a powered return stroke, connecting rod is still connected to piston. However, both sides of piston are in contact with working fluid, In embodiments that include powered return stroke, end of cylinder that connecting rod 200 projects from must be sailed bv seal 202 to ma.intAn pressure of working fluid for powered return stroke. As shown in Figure 14a, force of working fluid on side of piston that is attaThed to connecting rod 2CO will only be. nrsnuttsd to that piston 192 surrounding connecting rod. This causes a reduced effective force being delivered to crank shaft. This reduction in service ares cf piston may be compensated for by increasing capacity and speed with which heat is transferred to working fluid. Figure 15 shows an alternative embodiment of a rmal hyd engine that includes a flexible blind flange. According to this embodiment, force generated, indicated by arrows in Figure 16, by expanding working fluid applies force to flexible blind flange 204 flange n acts upon, member 2U6', reby displacing member 206. Movement of member 206 may be guided by guide 207.. Member 20G is interconnected with a crankshaft or or drive mechanism (not shown in Figure 16) , flange 204 may bs secured between two mounting flanges 208 and 210 similarly to embodiment shown in Figure 12 . Regardless of wher engine includes a powered return stroke, connecting rod may be fixably or movably attaThed to piston. If connecting rod is fixably attaThed to piston, n cylinder preferably is articulately mounted to frame. Regardless of wher connecting rod is movably or fixably attaThed to piston, connecting rod may include one or more sections. connecting rod may be connected to a crank shaft and or transmission elements to drive a device or an electric generator. In some embodiments, cylinder is fixedly attaThed to a frame and connecting rod articulately attaThed to piston and a crank shaft so that as piston moves back and forth through its stroke and crank shaft rotates, connecting rod will change its position. As shown in Figs. 23A23H and 24, cylinders of rmal hydraulic engine according to present invention may be arranged radially. Utilizing a radial arrangement of cylinders in rmal hydraulic engine may permit a more immediate transfer of energy from cylinders to crankshaft and whatever load is being placed on engine. Additionally, a radial arrangement of cylinders may provide a more direct path through mechanical system of engine for forces generated by working fluid. Furrmore, back pressure, discussed in greater detail below, and or internal loads from piston and/or piston 0rings may be more directly handled by power stroke of engine with radially arranged cylinders. An embodiment of a rmal hydraulic engine according to present invention that includes radially arranged cylinders may include any number of cylinders. number of cylinders in an embodiment of present invention that includes a radial arrangement of cylinders may be an even number or an odd number. embodiment of rmal hydraulic engine according to present invention shown in Figs. 23A23H and Fig. 24 includes four cylinders 300, 302, 304, and 306. cylinders may be attaThed to frame 299. pistons (not shown) within cylinders are connected through crank arms 308, 310, 312, and 314 to a connecting member 316. To facilitate rotation of crankshaft and connecting member 316, connection between crank arms 308, 310, 312, and 314 may be articulately mounted to pistons (not shown) located within cylinders 300, 302, 304, and 306 or to connecting member 316. connecting member 316 may be interconnected through connecting member 318 to crankshaft 320. Figs. 23A23H illustrate various positions of pistons, connecting arms, connecting members, and crankshaft throughout a revolution of engine, as cylinders experience both power and return strokes. In Fig. 23A, piston 300 is in its power stroke. Piston 302 is just beginning its power stroke. Additionally, piston 304 has completed its cooling or return stroke. On or hand, piston 306 is in beginning stages of its cooling, or return, stroke. In view shown in Figs. 23A23H, crankshaft is rotating in a clockwise direction. Piston 304 has completed its cooling cycle on its return stroke and is beginning its heating cycle, but has not yet reaThed its power stroke range. By saying that piston has not reaThed its power stroke, it is meant that working fluid has not reaThed a pressure capable of moving piston at all or more than an insubstantial amount along its power stroke. In or words, pressure is not in a range to move piston and piston is not physically in range of its power stroke. Fig. 24 shows a threedimensional perspective view of embodiment of rmal hydraulic engine shown in Figs. 23A23H. As can be seen in Fig. 24, cylinders may be mounted to frame members 322, 324. Piston mounting frame members 322 and 324 typically are mounted to anor structure or structures to secure m. In any embodiment of present invention, and particularly, in an embodiment that includes a radial arrangement of cylinders, cooling cycle of any one piston preferably permits shrinking of working fluid at a rate equal to or faster than expanding of working fluid in a piston that is in its power stroke during return stroke The piston in question. If cooling of working not as rapid as incre ir. t sixers tur» in rkiiiy fluid, trv? •cikjnq trtjback prassura" that rwvy restrict The rcvecr pis.cn in its power stroke. back pressure may create an unnecessary load 01 tha engirt, hindering entire operation cl engine. This is particularly case in an evobcdi.Tier. an sngine ciccording to The! present: invention chat includes a radial arrangement of ny lenders since cylinders ars typically d in oppo.inc pairs. If one cylinder experiences a back pressure as a resul ; rapid cooling and shrinking of working fluid, as couipared to heating and expansion of working fluid, in anor cylinder undergoing its power stroke at The same tine, cylinder undergoing its pcwsr stroke will be inhibited in its movement by back pressure. As such, back pressure acts as an additional load on engine ir. addition to whatever lead, such as a pump or or device that engine is driving, One way to help prevent, occurrence of back pressure is to ensure that heat is removed from ths working fluid quickly enough. This may be accomplished by ensuring a flow of cooling fluid sufficiently rapid to result in a removal of hedt from ths working fluid in cylinder uridsx'going a return stroke at: rate equal to or greater than transmission of hsat to working fluid in cylinder undergoing a power stroke. If, as describe herein, engine does not include heat exchangers, n preferably, rate of heat transfer from working fluid in cylinder undergoing return stroke is equal to or greater than rate of transmission of heat to working fluid in cylinder undergoing power stroke. Removal and transmission of heat may be dependent upon characteristics of working fluid, cooling source material, heat exchanger, among or factors. transmission elements are n connected to a load to perform a desired function. For example, engine could power a water pump, an electric generator, and/or a FREON compressor, among or elements. In order to transmit heat to and remove heat from working fluid, working fluid container preferably is in communication with means for transmitting heat to and removing heat from working fluid contained in working fluid container. same means may perform both heating and cooling. Alternatively, present invention could include separate means for performing each function. According to one embodiment, means for transmitting heat to and removing heat from working fluid is a heat exchanger. Depending upon wher it is desired that working fluid be heated or cooled, relatively warmer or relatively cooler water or or material may be introduced into heat exchanger. Preferably, a rmal hydraulic engine according to present invention includes one heat exchanger for each working fluid container, although an engine according to present invention could include any number of heat exchangers. Figure 11 shows an embodiment of heat exchanger or working fluid container according to present invention. According to this embodiment, working fluid container 176 is surrounded by heat exchanger 178. This heat exchanger includes two openings, an inlet and an outlet. A relatively hotter or cooler material may be introduced into heat exchanger to heat or cool working fluid. Wher working fluid is heated or cooled depends at least in part upon wher material in heat exchanger is relatively hotter or cooler than working fluid. working fluid container may include a plurality of fins or or devices to increase surface area of working fluid container in contact with material introduced into heat exchanger. Among or alternatives for increasing heat transfer to working fluid is including a circulation pump in working fluid container. A circulation pump can create turbulent flow for increased heat transfer speed. heat exchanger is one example of a means for transmitting heat to or removing heat from working fluid. heat exchanger can be built around working fluid container wher part of a containment system or not. In a heat exchanger, typically, high and low temperature fluids are brought into contact with working fluid container. Typically, fluid circulating through heat exchanger is under relatively low pressure. However, working fluid changes temperature, depending upon wher it is desired to heat or cool working fluid. refore, heat exchanger preferably is also constructed of a material capable of withstanding pressures and temperatures that fluid circulating through it is at. Examples of materials that may be utilized in heat exchanger are polyvinylchloride (PVC) pipe, metal pipe such as carbon steel, copper, or aluminum, cast or injected molded plastic, or a combination of any materials capable of withstanding pressures and temperatures involved in heat exchanger. It is not necessary that only a liquid be utilized in heat exchanger to transmit heat to or remove heat from working fluid. For example, gases or a combination of liquid and gases may also be used in heat exchanger to heat and/or cool working fluid. One advantage of present invention is that any high and low temperature source material, wher liquids, or gases or transmitted by anor means may be used to heat and cool working fluid. For example, heated waste water from industrial processes could be used to transmit heat to working fluid. Such water typically is cooled in some manner before being discharged to environment. refore, rar than being wasted, heat in this water could be utilized in present invention to produce mechanical and/or electrical energy. As stated above, solar heating and cooling could also be used according to present invention. It is this ability to utilize heat and cooling from unutilized sources, such as waste heat, or free sources, such as sun, that makes present invention so desirable. If a fluid is used in heat exchanger, preferably, liquid and/or gas should be under at least some amount of pressure to ensure that liquids and/or gases flow through heat exchanger. As heated liquid and/or gas moves through heat exchanger, it will transfer its greater heat energy to working fluid having a lower heat energy. working fluid will n expand, applying force against a piston, flexible barrier or or member, reby producing mechanical energy. When working fluid has absorbed as much heat as is possible or as is desired from heat exchanger, a relatively cooler liquid and/or gas may be transferred through heat exchanger. heat in working fluid will n, according to natural laws, flow to relatively cooler liquid and/or gas in heat exchanger. Figure 22 shows an alternative embodiment of a heat exchanger according to present invention. According to this embodiment, heat exchanger 212 is located within working fluid container 214. According to this embodiment, working fluid container is also continuous with piston. According to or embodiments that include heat exchanger within working fluid container, working fluid container may not be continuous with cylinder. In Figure 22, distance a represents travel of piston between its maximum positions at power and return strokes. end 216 of working fluid container 214 may be sealed with a flange 218 secured between a flange 220 on working fluid container and an end flange 22 secured to working fluid container flange 220 with bolts 224. Figure 5 shows a simple version of a three cylinder engine according to present invention. components shown in Figure 5 may not necessarily be in same physical position in relation to each or in engine and are shown here in this arrangement for ease of understanding. engine may also include or components not necessary include in se embodiments or shown in this Figure. engine shown in Figure 5 includes three cylinders 100, 102 and 104. A piston 106, 108, and 110, respectively, is disposed within each of cylinders. Each of pistons is connected to a connecting rod, 112, 114, and 116, respectively, that is connected to a crank shaft 118. number of cylinders and pistons included in invention may vary, depending upon embodiment and factors described above. An engine utilizing a piston such as that shown in Figures 14 and 15 may utilize only two cylinders and pistons since pistons will be pushed back into cylinder by working fluid entering side of cylinder where piston is attaThed to connecting rod. This is because re is less of a need to maintain speed of engine to ensure that pistons will travel back into cylinders than is necessary when a power a return stroke is not utilized. Accordingly, without utilizing power return stroke and only utilizing forward power stroke, it is preferable that engine include at least three cylinders. Due to slow moving nature of pistons in an engine according to present invention, it may be necessary to include three pistons to ensure that pistons will complete ir return stroke. With three pistons, at least one piston will always be in a power stroke, to help ensure that or piston will help complete ir return stroke. This occurs because one piston is always in power stroke will be furring rotation of crank shaft reby helping to move or pistons along ir return stroke. However, an engine according to present invention may include any number of cylinders. For instance, engines can be built with 16, 20, or more cylinders for larger electric power plant operations. crank shaft is interconnected with a load. load could be a mechanical device driven by crank shaft. Anor example of a load could be an electric generator that is driven by crank shaft. crank shaft is also connected to a water valve 122 that controls flow of high and low temperature liquid and/or gas into heat exchangers. cylinders 100, 102, and 104 are each interconnected via a high pressure hose, 124, 126, and 128, respectively, to a working fluid container, 130, 132, and 134, respectively. working fluid containers 130, 132, and 134 are enclosed within heat exchangers 136, 138, and 140, respectively. working fluid may be contained within space defined by heat exchangers 130, 132, and 134, high pressure connectors 124, 126, and 128 and interior of cylinders 100, 102, and 104. Of course, in embodiments that include a fluid containment system, working fluid is contained within working fluid container. As is evident, in embodiments without working fluid containment system, space that working fluid is contained in changes volume as piston moves within cylinder. Figure 6 shows a series of depictions of three cylinder engine shown in Figure 5 as cylinders cycle. In embodiment shown in Figure 6, 141 represents an offcenter lobe cam with rocker arm lever and/or push rods to push open water valves. cam shaft controls flow of heat and cooling to working fluid. Each cylinder/heat exchanger/working fluid container is represented by 1, 2, and 3 . flow of heating and cooling is represented by high temperature water flow into system 142, low temperature into system, 144, high temperature return 146, and low temperature return 148. Flow from source of high temperature to system is represented by 150, flow of low temperature from low temperature source to system is 152, flow from system to source of high temperature is represented by 154, and flow from system to source of low temperature is represented by 156. As cylinders cycle as shown in Figure 6, high and low temperature fluid flows in and out of heat exchangers depending upon wher particular cylinder involved is moving in one direction or anor. As shown in Figure 5, opening and closing of valves directing high and low temperature fluid into heat exchanger may be controlled by a cam shaft directly or indirectly connected to a crank shaft driven by cylinders. An indirectly connected cam shaft could be connected to crank shaft with a timing chain type connection. Of course, any connection could be used to connect cam shaft to crank shaft. cam shaft could be an offcenter lobe cam with rocker arm lever and/or push rods to push open water valves leading to heat exchangers. Figure 7 shows an embodiment of a rmal hydraulic engine according to present invention that includes four cylinders 158, 160, 162, and 164. valves 166 and 168 transmitting hot and cold fluid to and from heat exchanger are directly controlled by crank shaft 170. In Figure 7, piston 158 is in process of beginning its power stroke. Hot fluid is flowing into heat exchanger 172 associated with piston 158 and also being withdrawn from heat exchanger 172. Circulating pumps may be driven directly from crankshaft power directly or indirectly. Indirectly driven circulation pumps could be driven through hydraulic pumps and/or motors. cooler fluid, in this case water used to cool working fluid may be obtained from water pumped out of a well by engine. As is seen in embodiment shown in Figure 4, 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 may be self sufficient and not require any outside power. Of course, such an embodiment could be connected to a power line to drive pump during times of insufficient light, wher during cloudy days or at night. Alternatively, batteries could be provided to drive circulation pump at such times. Figure I shows a general sThematic drawing of a power . utilising a rmal hyda KU accreting to temperature source 3, a heat exchanger 5, a rmal hydraulic engine 7, which, in this case, refers to working fluid and cylinder mselves, a transmission. 5 of some type, perhaps a flywheel 11 tc maintain csotcentum of ths engine, and an electric generator 13. Of course, power plane need not necessarily irzdude a flywheal and need not derive ar. electric generator. power plant could also include additional ccrapor.ejits not snown in Figure 1 and/or not included in embodiment shown in Figure 1. Figure 2 shows an embodiment of a rmal hydraulic engine that utilizes solar energy to provide heat to heat working fluid and an evaporative cooling system to remove heat from working fluid. Figure 2 illustrates flow of heating and cooling water through various components of system. Of course, a material or than water may be utilized to heat and cool working fluid, As cooling water enters one heat exchanger associated with one cylinder, to draw heat out of system, hot water that is created as cooling water absorbs heat from working fluid may be recirculated to a hot water reservoir, if system includes a reservoir. system shown in Figure 2 includes solar hot water panels 2 to heat water that will cause expansion of working fluid. Water heated by hot water panels will flow through at least one water directing valve 4 that directs heated water to a hot water reservoir 6. From hot water reservoir 6, heated water will flow to a hot water pump 8. hot water pump 8 will circulate heated water to rmal hydraulic engine (not shown) and n back to solar hot water panels 2 to be heated again. embodiment shown in Figure 2 also includes an evaporative cooling system 10 to provide water that is cooler than water heated by solar hot water panels 2 to remove heat from working fluid. Water cooled by evaporative cooling system 10 flows out of evaporative cooling system through at least one water directing valve 4. water directing valve directs cooled water to a cool water reservoir 12. From cool water reservoir 12, cooled water will flow to a cool water pump 14. cool water pump 14 will circulate cooled water to rmal hydraulic engine (not shown) and n back to evaporative cooling system 10 to be cooled again. Figure 3 shows an embodiment of interconnection between crank shaft 15, driven by rmal hydraulic engine (not shown in Figure 3) , and elements making up load on engine. In this embodiment, crank shaft 15 is connected to a chain drive gear and sprocket 17 that includes two relatively large gears 19 and 21 connected to ultimately to a smaller gear 23. As can be appreciated, rotation of crank shaft 15 will be greatly magnified by gear in embodiment shown in Figure 3. Figure 3a shows an enlarged side view of chain drive gear and sprocket 17, showing gears 19, 21, and 23 and chains 20 and 22 driven by and driving gears. chain drive gear may be connected to a hydraulic pump 25 and motor gear up 27 which is ultimately connected to an electric generator 2y. A flywheel 31 may be interconnected between hydraulic pump and motor gear up to help maintain cycling of engine. Figure 4 vewrsrx a schsiiatic view of anor embodiment of a solar powered rmal hydraulic engine and some associated elerneiits according to present invention. Heat is delivered to and. removed from working fluid by relatively hotter cooler wats::. As with any embodiment, a material or than may be used to deliver heat to and remove heat from ths working fluid. Figure 4 also shows flow of heatid wat:?r through ay stem. embodiment shown in Figure 4 includes rmal hydraulic engine 33.. Solar panels 3i provide heat that heats working fluid tha engine. heated water n travels to a series cf vajvet' 37, 39, 41, and 43. number of valves may depend upon number of cylindex's in engine, number of heat exchangers, and how water is distributed to heat exchangers and cylinders, among or factors. valves 37, 39, 41, and 43 deliver water to heat exchanger(s) 45. heated water n heats working fluid in engine 33. After delivering its heat to working fluid, heated water is directed through valves 47, 49, 51, and 53 and n back to solar array 35. A circulating pump 55 drives flow of heated water. circulation pump 55 may be powered by electricity generated by photovoltaic cells (not shown). rmal hydraulic engine 33 may be connected to transmission 57. In this embodiment, engine 33 drives a pump 59. pump 59 may be utilized to pump water from a water source 61. water source 61 may include a well, reservoir, or tank, among or sources. water may be pumped from water source 61 into a water storage pipeline 63. Water from water source 61 may be utilized as source of cooling water for cooling working fluid as well as a source of water to be heated to provide heat to working fluid. Water for eir function may be stored in a storage tank 63. components of engine according to present invention may mounted on a frame. Figure 21 shows an embodiment of a rmal hydraulic engine according to present invention that includes four cylinders wherein components of engine are mounted to a frame A. To simplify explanation of operation of present invention, functioning of a three cylinder engine according to present invention will be described. Figure 5 shows an example of such an embodiment. working fluid is contained within cylinder and working fluid container is surrounded by heat exchanger. refore, in a sense, heat exchanger acts as a containment system. Given fact that re are three cylinders 67, 69, and 71 and three pistons 73, 75, and 77 in embodiment described here, each piston preferably powers crank shaft 79 about a rotation of at least 120°, so that one piston is always in operation powering crank shaft rotation. operation of engine will be described with assumption that one piston will be starting its power stroke. To begin power stroke, working fluid must be heated. embodiment shown in Figure 5 includes three heat exchangers 132, 136, and 138 to introduce heat to and remove heat from working fluid. difference between working fluid in a heated state and a cool state may vary, depending upon embodiment. According to one embodiment, difference between high temperature of working fluid and low temperature of working fluid is about 4060°F. However, differential between high and low temperatures of working fluid may be larger or smaller. high temperature of working fluid may be anywhere from about 80200°F. range of temperatures of high temperature of working fluid may also be from about 120 140°. However, any temperature for high temperature of working fluid could be utilized as long as it is higher than lower temperature of working fluid. In fact, superheated water above 212°F could also be utilized. low temperature of working fluid could vary from about 35°F to about 85°F. According to one embodiment low temperature may be from about 70° to about 85°F. However, as stated above regarding high temperature, low temperature of working fluid may be any temperature, as long as it is lower than high temperature of working fluid. greater differential in high and low temperatures, greater possibility for heating cooling working fluid. temperature of working fluid may also be defined by defining highest temperature of working fluid relative to lowest temperature of working fluid. Accordingly, difference in temperatures of working fluid may be up to about 60°C. Alternatively, difference in temperatures of working fluid may be between about 60°C and about 120°C. Or ranges for difference in temperatures of working fluid include between about 120°C and about 180°C and between about 180°C and about 240°C. Prior to starting operation of engine, working fluid may be pressurized to help maintain a seal between piston and wall of cylinder. A positive pressure maintained in cylinder may help to force a seal in area between piston and cylinder. For example, working fluid could be prepressurized to about 200 Ibs. per square inch. If working fluid is prepressurized, it may be pressurized to an extent such that during contraction of working fluid as heat is removed from working fluid, pressure within cylinder never drops below 0. However, it is not necessary that working fluid be prepressurized at all. Figure 10 represents a graph showing operating range of temperatures and pressures that an embodiment of a rmal hydraulic engine utilizing a working fluid. As working fluid is heated and it starts to expand, force of fluid is transmitted to piston, reby moving piston. According to one embodiment of present invention including three cylinders, rotation of crank shaft does not begin until connecting rod 174 has moved to a point about 20° past top dead center as shown in Figure 8. As stated above, in a three cylinder embodiment, piston must power crank shaft around at least 120° since re are three pistons and 360° in a complete rotation of crank shaft. Similarly, in a four cylinder engine, each piston must power crank shaft about 90°. corresponding number of degrees that piston must power crank shaft rotation may be calculated simply by dividing 360° by number of pistons. Given fact that rotation of crank does not commence until connecting rod has moved about 20° beyond top dead center, calculation of 120° of power stroke of piston will be calculated from this 20° starting point of rotation. However, power stroke of next piston will be started upon connecting rod reaching 120° beyond top dead center. refore, re will a 20° overlap between power stroke of first cylinder and second cylinder. This will help to ensure a smooth transition between pistons with effective turning force being transmitted to and from crank shaft being maintained thoroughly constant. smooth transition of power is assisted by fact that as any piston is traveling through its power stroke, it not only powers rotation of crank shaft or or device that harnesses movement of piston but it may also help to drive or pistons in engine on ir return stroke. As shown in Figure 9, heat source associated with first cylinder preferably is cut off when connecting rod reaThes about 120° beyond top dead center, according to this embodiment. Next, source of cool fluid is started into heat exchanger when connecting rod reaThes about 140° beyond top dead center. As return stroke of first piston continues and rotation of connecting rod and crank shaft continue, when connecting rod reaThes about 300° beyond top dead center, source of cold fluid to heat is turned off and source of high temperature fluid to heat exchanger is started again. points at which sources of high and low temperature fluid are introduced into heat exchanger may vary, depending upon embodiment of invention. One factor that may alter flow of high and low temperature fluid into exchanger is wher or not working fluid is prepressurized as described above. speed of movement of piston and, hence, crank shaft may be increased by increasing flow of high temperature fluid into heat exchanger. speed of operation of engine and horsepower output may also be increased by increasing temperature differential between high and low temperature fluids introduced into heat exchanger and, hence working fluid. At 300° rotation point, when source of high temperature fluid is reintroduced into heat exchanger, working fluid has come back to its base temperature pressure and volume. It is se volume, temperature and pressure parameters that are utilized to calculate engine size, flow of high and low temperature fluid to heat exchanger, engine load, cylinder size, cylinder number, and many or operating and design parameters of invention. . flow of high and low temperature fluid into heat exchanger described above may be controlled in a variety of ways. For instance, a timing gear may be directly or indirectly connected to crank shaft. timing gear may n mechanically actuate valves that control flow of high and low temperature fluid into heat exchanger based upon position of crank shaft. Alternatively, a cam shaft rotated by crank shaft may operate an electrical system that electrically controls flow of high and low temperature fluid into heat exchanger. Or methods that may be utilized to control flow of high and low temperature fluid into heat exchanger can include lasers, computer programs, optical devices, mechanical push rods, connecting rods, levers, or or manual and/or automatic devices. As will be appreciated, a complex computer control could optimize operation of a rmal hydraulic engine according to embodiment, just as electronic control has helped to optimize operation of internal combustion engines in modern automobiles. A complex electronic control system can simultaneously monitor and control a wide variety of parameters, optimizing .operation of engine. As stated above, rmal hydraulic engine of present invention may include a mechanical valve for directing flow of working fluid and or fluids. Fig. 31 shows one example of a rotating valve that may be utilized to direct flow of coolant and/or working fluid in a rmal hydraulic engine according to present invention. valve shown in Fig. 31 includes a connector 560 connected to a valve body 562. valve body houses a valve rotor 564 that rotates within valve body. Valve rotor 564 includes a plurality of outlets 566, 568, 570, and 572. Valve body 562 may be connected to an anchor block 574 or or structure to anchor valve. valve body and valve rotor may be kept by a cap 576. Valve body 562 also includes outlets 578, 580, 582, and 584. Outlets 578, 580, 582, and 584 are connected to outlet pipes 586, 588, 590, and 592. Valve body outlets 578, 580, 582, 584 are also aligned with rotor valve outlets 566, 568, 570, 572, such that as valve rotor rotates and outlets 566, 568, 570, and 572 are aligned with valve body outlets 578, 580, 582, and 584, coolant, working fluid, or or fluids will flow to desired location. valve rotor 564 may be turned through geared operation of a timing chain connected to main shaft of crankshaft. embodiment shown in Fig. 31 includes sprockets for connecting to timing chain. Rar than rotating valve, flow of fluids in present invention may be controlled mechanically with use of or types of valves, including cam/pushrod/rocker arm time mechanisms. flow of fluids may also be controlled with an electric solenoid valve. Any or valve may also be utilized to direct flow of fluids in present invention. Additionally, a rotating valve such as that shown in Figure 31 may be included in any engine according to present invention. rmal hydraulic engine according to present invention may include an engine cranking system with pistons operating independently of each or. In typical inline, Vtype, or radially designed engines, each piston is mechanically connected to each of or pistons. Internal combustion engines use this mechanical reliance to push exhaust gases out of. engine, pull fresh gas into piston chamber, and pressurize gas prior to combustion. However, less mechanical reliance may be required in a rmal hydraulic engine according to present invention. For example, if cylinders include two ports, mechanical interconnection of all pistons may not be necessary. return of piston in such systems is typically accomplished mostly by pressurization of opposite side of piston. This return mechanism also supplies crankshaft drive power. present invention may utilize a crankshaft that can be turned by a free releasing arm mechanism that is able to slide freely around crankshaft in a return direction, lock onto crankshaft in a forward or power direction. Figs. 3235 show an example of such a crankshaft. crankshaft shown in Figs. 3235 includes a ratThettype mechanism. shaft shown in Figs. 3235 can be used in conjunction with multiple crank arms to provide a continuously turning shaft. Fig. 32 shows a crank arm 587 connected to a crankshaft 589. crankshaft 589 includes an indentation 591 that receives a portion of crank arm 587. As can be seen in Fig. 32, crank arm 587 will cause a rotation of shaft 589 up until point that crank arm 587 slips out of recess 591. Preferably, crank arm 587 will no longer engage recess 591 at a point substantially near end of power stroke of a piston connected to crank arm 587 so that power of piston is substantially and entirely communicated to crankshaft 589. crank arm 587 will n ride along a surface of crankshaft 589 as piston is on its return stroke. As piston again begins its power stroke, crank arm 587 will n start to travel back along surface of crankshaft until it engages a recess. Fig. 33 shows an embodiment of a ratThettype crankshaft illustrating position of a crank arm throughout a power cycle of a piston. Fig. 34 represents an embodiment of a cylinder, crank arm, and crankshaft including a ratThettype movement mechanism. Fig. 34 also illustrates various positions of crank arm during movement of piston. Fig. 35 shows anor embodiment of a crank arm and crankshaft utilizing a ratThettype mechanism. Fig. 36 shows a crank moment arm that includes stiffening ribs 599 to reinforce crank moment arm so furr ensure that it can withstand great pressures generated by present invention. . ' Rar relying upon heat exchangers, heat may be imparted to working fluid directly. An example of an embodiment of a rmal hydraulic engine according to present invention that includes direct transmission of heat to working fluid is shown in Fig. 27. embodiment shown in Fig. 27 includes four radially arranged cylinders. engine includes a centrally located rotating valve 360 to which each cylinder is connected. Each cylinder is also connected to a working fluid reservoir to which heat is directly imparted. Directly heating working fluid does not utilize a heat exchanger and it does not use heated liquid to transfer heat from a heat source to working fluid. direct transfer method directly heats working fluid with heat source. As can be appreciated, re is no loss of heat associated with use of heat exchangers. Fig. 28 provides an example of an embodiment of a working fluid container that may be utilized in a rmal hydraulic engine utilizing direct heat transfer. working fluid container or reservoir shown in Fig. 28 includes an elongated tube 348. Although working fluid container may have any desired shape, it may include a large amount of surface area relative to volume so as to increase rate of heat transfer to working fluid. embodiment of working fluid container shown in Fig. 28 includes a 20 ft. long pipe that is 4 inThes in diameter made of "SThedule 80" pipe. pipe may include an assembly 350 for joining pipe to conduit for connecting working fluid reservoir to cylinder. Fig. 29 shows an end view of pipe, shown in Fig. 28, showing a flange 352. Flange 352 may include a plurality of holes 354 for utilizing bolts 356 to connect flange to anor flange for connecting to a conduit for connecting to cylinder. embodiment of working fluid reservoir shown in Figs. 27 and 28 also includes cooling element 358 inserted into pipe 348. A cooling fluid may be introduced into conduit 358 to cool working fluid. conduit 358 may be interconnected with rotating valve 360 for directing cooling fluid to relevant working fluid reservoir. In order to accommodate high pressures inherent in some working fluids, cooling fluid conduit 356 preferably is made of a material capable of withstanding high pressures. According to one embodiment, 3A inch high pressure steel pipeline is utilized. Although pressure of working fluid may be high, pressure of coolant may be low, for example, in one embodiment, pressure of coolant was from about 32 to about 80 psi. Fig. 30 shows a closeup crosssectional view of a connection between working fluid reservoir, coolant conduit 359, flanges 352 and 353, gasket 355, and bolts 357. In embodiment shown in Fig. 27, each of working fluid reservoirs 362, 364, 366, 368 is placed within a parabolic solar heat collector 370, 372, 374, and 376, respectively. solar heat collector imparts heat to working fluid. As working fluid expands, it powers cylinders. , At appropriate time, rotating valve 360 directs coolant into each of working fluid reservoirs. As coolant is circulated through working fluid reservoirs, it is heated. heated coolant is directed to a hotcold separator 378. To augment heat imparted to working fluid by solar heat collectors, present invention may direct heated coolant through coolant conduit 356. Hot cold separator 378 preferably separates flow of coolant from working fluid reservoirs undergoing expansion from coolant exiting working fluid cylinders undergoing contraction. Heat may be withdrawn from coolant in heat exchanger 380. Heat from coolant may be stored in heat storage device 382. Flow of coolant may be controlled by a plurality of pumps. embodiment shown in Fig. 27 includes an hydraulic motor coolant pump 384 for directing coolant from heat exchanger 380 to rotating valve 360. hydraulic motor coolant 384 may be driven by rmal hydraulic engine. present invention may also include hydraulic motor heat recycle pump 386. Hydraulic motor heat recycle pump 386 may pump coolant from heat storage device 382 to rotating valve 360. Hydraulic motor heat recycle pump 386 may also be driven by rmal hydraulic engine. embodiment of rmal hydraulic engine shown in Fig. 27 is shown being utilized to drive a hydraulic pump (not shown). Conduits 390 and 392 are for directing hydraulic fluid from hydraulic pump operated by rmal hydraulic engine to various loads that are desired to be driven by rmal hydraulic engine. As stated above, in embodiment shown in Fig. 27, hydraulic motor coolant pump 384, hydraulic motor heat recycle pump 386, and water pump 388 are driven by rmal hydraulic engine. Arrows on lines 390 and 392 indicate direction of flow of hydraulic fluid to loads. Operation of heat exchanger 380 may be enhanced by pumping water in conduits 394 and 396 into, respectively, water pumped by water pump 388. A rmal hydraulic engine according to present invention may be built in any size. For example, very small engines for use in applications such as biomechanical applications, to large megawatt power plants may incorporate rmal hydraulic engine of present invention. In fact, tne rmal hydraulic engine can be designed for use in any application that requires power of mechanical energy. A very small engine could include pistons about 0.5 cm to about 1 cm in diameter. Such an engine could include working fluid reservoirs about size of a typical body rmometer. In fact, such engines could utilize heat at about typical human body temperature as a heat source. Cooling could be provided by an external evaporative system. Such an engine could be used in human or or body. One example of a use for such an engine is as a heart pump. Anor example of an application is for hormone injection. For example, such an engine could be used for people with a failed lymphatic system. Such an engine could provide, for example, from about 0.01 horsepower to about 0.1 horsepower. On or end of spectrum, very large engines could be built within scope of present invention. For example, an engine that could generate about 350 million horsepower could provide about 500 megawatt electric generating capabilities. Such an engine could utilize a piston having a diameter of about 48 inThes to about 9o inThes. engine could be built in a heavily reinforced concrete and steel structure. An engine capable of pumping water could generate from about 10, about 50, about 200 horsepower or anywhere in between. Fig. 37 shows an embodiment of a one horsepower water pump powering a rmal hydraulic engine according to present invention. Heat to expand working fluid is provided by a parabolic solar heat collector 400; solar collector preferably includes a drive 402 for tracking movement of sun. working fluid is delivered to engine 406. Power produced by engine 406 is transmitted by transmission 408'to pump 409. invention may include control 410 for controlling flow of coolant. engine may also include battery 412 for providing power. Fig. 38 shows an overhead view of solar heat collectors 400. engine, shown in Figs. 37 and 38, includes direct rmal heat exchange tubes 414. A photovoltaic panel 416 may also be provided to provide electrical power for certain aspects of invention, such as tracking control and cooling control. Fig. 39 shows an embodiment of a seasonal tracking chain drive with counterweight that may be utilized to tilt solar array in proper position throughout year. embodiment shown in Fig. 39 may include chain drive 600, motor 602, and counterweight 604. motor may be an suitable motor. For example, motor could be a high torque, low rpm, 12 volt dc motor. Fig. 39 also shows normal position 606 of solar array. array pivots about pivot 608. pivot could be provided by a hinge or or pivotable device. Fig. 40 shows an embodiment of a rmal hydraulic engine according to present invention that utilizes electric heat as a source to impart heat to working fluid. embodiment shown in Fig. 40 includes four radially arranged cylinders. Fig. 40 also shows gearing that may be utilized to gear up power produced by engine. embodiment shown in Fig. 40 includes working fluid reservoirs 720 comprising 4 inch diameter, 24 inch long, pipe. Coolant is circulated through working fluid in % inch line 700. Heat is provided by an electric heat element 718 that may utilize 120 V AC power. coolant fluid reservoirs may be closed by a 2 inch welded neck flange 724. pistons 702, 704, 706, and 708 included in cylinders 710, 712, 714, and 716 in embodiment shown in Fig. 40 are two inThes in diameter and 8 inThes long. outside diameter of pistons 702, 704, 706, and 708 is 4 inThes. cylinders are radially arranged as in embodiment shown in Fig. 27. Fig. 40 also illustrates a plurality of gears and connecting belts or chains, collectively identified as122, that may be used to gear up power generated by rmal hydraulic engine. Fig. 41 shows an alternative view of engine shown in Fig. 40. Fig. 43 illustrates an embodiment of a rmal hydraulic engine according to present invention that includes a passive solar collector 900. Hoses 902 and 904 connect solar collector to a double acting cylinder 906. engine is used to pump water from a well. Fig. 44 illustrates represents a furr embodiment of a cylinder, piston and crank arm according to present invention. foregoing description of invention illustrates and describes present invention. Additionally, disclosure shows and describes only preferred embodiments of invention, but as aforementioned, it is to be understood that invention is capable of use in various or combinations, modifications, and environments and is capable of changes or modifications within scope of inventive concept as expressed herein, commensurate with above teachings, and/or skill or knowledge of relevant art. embodiments described hereinabove are furr intended to explain best modes known of practicing invention and to enable ors skilled in art to utilize. invention in such, or or, embodiments and with various modifications required by particular applications or uses of invention. Accordingly, description is not intended to limit invention to form disclosed herein. Also, it is intended that appended claims be construed to include alternative embodiments. We Claim: 1. A thermal hydraulic engine, comprising: a frame; a working fluid that changes volume with changes in temperature; a working fluid container for housing said working fluid; a cylinder secured to said frame and including an interior space, said cylinder also including a passage for introducing said working fluid into said interior space; a piston housed within said interior space of said cylinder, said working fluid container, said interior space of said cylinder, said piston, and said working fluid container defining a closed space filled by said working fluid; a connecting rod connect to said piston; a crankshaft connected to said connecting rod; characterized in that. means for controllably transmitting heat to and removing heat from said working fluid, thereby cyclically alternately causing said working fluid to expand and contract without undergoing a phase change, said piston moving in response to said expansion and contraction of said working fluid, said expansion and contraction of said working fluid being unobstructed by valves. 2. A thermal engine according to claim 1, comprising: a working fluid transfer section between said working fluid container and said interior space of said cylinder, said working fluid container, said working fluid connection, said interior space of said cylinder and said piston defining a closed space filled by said working fluid. 3. A thermal hydraulic engine according to claim 1, comprising: a plurality of cylinders, each of said cylinders housing a piston, a plurality of working fluid containers interconnected with said cylinders, and a plurality of heat transmitting means interconnected with said working fluid containers and said cylinders. 4. A thermal hydraulic engine according to claim 1, comprising: means for mounting said cylinder to said frame, said mounting means permitting said cylinder to slide and articulate relative to said frame, said mounting means having a connecting rod provided on said cylinder, said connecting rod being articulately secured to a member slidably mounted to said frame, said slidable member sliding in a direction perpendicular to a crankshaft interconnected with said connecting rod. 5. A thermal hydraulic engine according to claim 1, comprising a water jacket that surrounds said working fluid container, said water jacket having an input and output for water of different temperatures to impart or remove heat from said working fluid through said heat exchanger. 6. A thermal hydraulic engine according to any preceding claim, comprising: a camshaft, wherein movement of said camshaft is controlled by said crankshaft and controls opening and closing of valves or opening and closing microswitches that activate solenoid valves for controlling transmission of heat to and removal of heat from said working fluid. 7. A thermal hydraulic engine according to claim 6, wherein said connecting rod is articulately attached to said piston. 8. A thermal hydraulic engine according to claim 6, wherein said connecting rod is immovably affixed to said piston and said cylinder is articulately mounted on said frame. 9. A thermal hydraulic engine according to claim 6, comprising: transmission means to increase or step up speed from the crankshaft. 10. A thermal hydraulic engine according to claim 6, comprising: at least one seal between an outer surface of said piston and an inner surface of said interior space of cylinder. 11. A thermal hydraulic engine according to claim 1, wherein said heat transmitting means is capable of raising a temperature of said working fluid to produce a high temperature of between about 120 degree and about 140 degree F., and said heat transmitting means is capable of reducing a temperature of said working fluid to produce a low temperature of between about 70 degree and about 85 degree F. 12. A thermal hydraulic engine according to claim 1, wherein said heat transmitting means is capable of raising a temperature of said working fluid to produce a high temperature of between about 80 degree and about 200 degree F., and said heat transmitting means is capable of reducing a temperature of said working fluid to produce a low temperature of between about 35 degree and about 140 degree F. 13. A thermal hydraulic engine according to claim 1, comprising: two connecting rods attached to opposite sides of said piston; and two crankshafts, one attached to each of said connecting rods. 14. A thermal hydraulic engine according to claim 1, wherein said piston and said interior space of said cylinder define two closed spaces filled by said working fluid, said cylinder further having: a main inlet port in the vicinity of a first end of said cylinder; a secondary inlet port 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 engine having at least one seal between an outer surface of said piston and an inner surface of said interior space of cylinder; wherein expansion of said working fluid is utilized to alternately move said piston in opposite directions. 15. A thermal hydraulic engine according to claim 1, wherein said working fluid is pressurized. 16. A thermal hydraulic engine according to claim 1, comprising means for mounting said cylinder to said frame, said mounting means permitting said cylinder to slide and articulate relative to said frame, said mounting means having a connecting rod provided on said cylinder, said connecting rod being articulately secured to a member slidably mounted to said frame, said slidably member sliding in a direction parallel to said cylinder. 17. A thermal hydraulic engine according to claim 1, further comprising at least one spring biasing said piston to move in a direction opposite to a direction that expansion of said working fluid causes said piston to move. 18. A thermal hydraulic engine, comprising: a frame; a first working fluid that changes volume with changes in temperature; a working fluid container for housing said first working fluid; a flexible diaphragm provided at one end of said working fluid container, said flexible diaphragm moving in response to expansion and contraction of said working fluid. a reservoir for housing a second working fluid in contact with said flexible diaphragm; means for transmitting heat to and removing heat from said first working fluid, thereby alternately causing said working fluid to expand and contract, expansion and contraction of said first working fluid causing movement of said flexible diaphragm, movement of said flexible diaphragm causing movement of said second working fluid; a cylinder secured to said frame and having an interior space, said cylinder also having a passage for introducing said second working fluid into said interior space; a piston housed within said interior space of said cylinder, said working fluid reservoir, said interior space of said cylinder, and said piston defining a closed space filling by said second working fluid.

Documents:

3678-del-1998-abstract.pdf

3678-del-1998-claims.pdf

3678-del-1998-correspondence-others.pdf

3678-del-1998-correspondence-po.pdf

3678-del-1998-description (complete).pdf

3678-del-1998-drawings.pdf

3678-DEL-1998-Form-1.pdf

3678-del-1998-form-19.pdf

3678-del-1998-form-2.pdf

3678-del-1998-form-29.pdf

3678-del-1998-form-3.pdf

3678-del-1998-form-4.pdf

3678-del-1998-gpa.pdf

3678-del-1998-petition-137.pdf