detailed crank shaft description

7/28/2019 Detailed Crank Shaft Description

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Detailed Crank Shaft Description

We can supply a diverse range of crank shafts available in more than

20 series and 50 different specifications.

Low Level Heat Powers Low Cost Hydraulic Engine

Deluge, Inc. has developed a thermal hydraulic engine that is now readyfor commercialization. The company has just successfully completed longterm field testing of the technology, and has obtained patents on the designin nearly 40 industrialized countries world wide.

The Natural Energy Engine, requires no combustion, operates virtuallysilently, and generates no emissions. Developed over the past 10 years, itoperates by utilizing low level heat energy, 180F (82C) is suitable formany applications, from solar, geothermal, or any other heat source,including waste heat from existing processes.

The main components of the engine system are quite simple apiston/cylinder and a heat transfer system. The cylinder contains a pistonand a working fluid, and depending on the application may have a moduleto reposition the piston after each stroke. The heat transfer systemcomprises heat exchangers, a system to circulate the heat transfer fluid(typically water), and a simple circulation controller.

The key difference between a traditional combustion engine and the NEEngine is that the NE Engine relies on the transfer of heat to, and itssubsequent removal from, a working fluid within the cylinder. As theworking fluid is heated it expands, providing the pressure to drive thepiston, and is subsequently cooled to complete the cycle.

It is a thermal hydraulic engine, says Brian Hageman, the inventor of theNatural Energy Engine. It uses the same principles of expansion andcontraction from heat as a thermometer, and uses the expansion to create


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powerful hydraulic pressure in a manner similar to an automobilesbrakes.

The Company projects that engine configurations can easily be priced at60-85% of power systems that produce equivalent output.

The NE Engine creates mechanical energy in a three step process:

Step 1: Heated water is collected for many applications 180F issuitable.

Step 2: The hot water enters a heat exchanger where the heat is transferredto a working fluid. The working fluid, typically liquefied CO2, has a veryhigh coefficient of expansion, meaning that it expands and contractssignificantly, based on its temperature, while remaining in a liquid state.As the working fluid is heated, it expands, pushing a piston in the engines

cylinder.

Step 3: Cooling water generally in the range of 100 lower than the inputwater, with varying differentials depending on the application thenenters the heat exchanger causing the working fluid to contract, readyingthe piston for another stroke.

Proof of the engines operating principles was first demonstrated at theU.S. Department of Energys Rocky Mountain Oil Testing Center inWyoming, where a prototype engine successfully pumped crude oil fromunderground formations using geothermal energy as the sole source of

heat for operation.

In early 2006, Deluge embarked upon extensive field testing, conducting amulti-engine long term test under varying conditions in Kansas fields, andcompleted well over 100,000 hours of continuous operation over morethan a year. The results exceeded even Deluges expectations in terms ofreliability, costs, and performance.

NATURAL ENERGY ENGINE TECHNOLOGY

TheNatural Energy Engine is a thermal hydraulic engine that createspower by using the physical properties of heated fluids expansion to movea piston. The engines have very low or no fuel costs, no internal fuelcombustion, and produce no pollution.


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Using an innovative design, and backed by $10 million in R&D since1996, these engines provide large cost reductions, environmentaladvantages and other benefits over conventional methods of energyproduction. Extensive field testing has successfully proven the technology.

The Deluge Natural Energy Engines core technology is an innovation inengine design. It combines advanced, yet proven, mechanical engineeringand thermal dynamic technologies to produce mechanical energy.

As a hydraulic engine, it capitalizes on the same mechanical advantageembodied in such prosaic everyday applications as automobile brakes.However, instead stopping a two ton vehicle with just the pressure of ahuman foot on a brake pedal, this engine uses the expansion properties offluid when heated.

The main components of the engine system are quite simple a

piston/cylinder and a heat transfer system. The cylinder contains a pistonand a working fluid, and depending on the application may have a moduleto reposition the piston after each stroke. The heat transfer systemcomprises heat exchangers, a system to circulate the heat transfer fluid(typically water), and a simple circulation controller.

In a typical internal combustion engine, fuel is ignited in a cylinderresulting in expanding gases whose increasing pressure drives a pistoncreating usable mechanical energy. The NE Engine works on the samegeneral principle of creating pressure on a piston in a cylinder to producemechanical energy.

The key difference between a traditional combustion engine and the NEEngine is that the NE Engine relies on the transfer of heat to, and itssubsequent removal from, a working fluid within the cylinder. As theworking fluid is heated it expands, providing the pressure to drive thepiston, and is subsequently cooled to complete the cycle. The expansionand contraction of the working fluid is based on the same principle seen ina traditional thermometer that causes the mercury to expand when heatedand contract when cooled.

Because it operates on temperature differentials, the engine also requires a

heat source and a method of removing the heat. The heat source can rangefrom waste heat to solar to geothermal to a simple hot water heater and,where cooling water is unavailable due to high ambient temperatures, themethod of heat removal can be as simple as a small evaporative coolingunit.

The NE Engine creates mechanical energy in a three step process:


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Step 1: Heated water is collected for many applications 180F issuitable.

Step 2: The hot water enters a heat exchanger where the heat is transferredto a working fluid. The working fluid, typically liquefied CO2, has a very

high coefficient of expansion, meaning that it expands and contractssignificantly, based on its temperature, while remaining in a liquid state.As the working fluid is heated, it expands, pushing a piston in the enginescylinder.

Step 3: Cooling water generally in the range of 100 lower than the inputwater, with varying differentials depending on the application thenenters the heat exchanger causing the working fluid to contract, readyingthe piston for another stroke.

The back and forth movement of the piston creates mechanical energy

directly from heat energy. This motion can be harnessed to operate amotor or to perform other work. Even lower temperatures and differentdifferentials can be utilized, all of which attest to the versatility of theengine. A formula has been developed that establishes the ratio betweenthe volume of the heat exchanger and the volume required to displace thepiston for various fluids. This formula establishes design parameters fordifferent horsepower systems.

In typical applications, due to the natural pressure of liquid CO2, thecylinder is constructed such that the CO2 working fluid is on one side ofthe piston and a pneumatic spring charged with nitrogen (N2) is on the

other. Heating the working fluid results in increased pressure on theworking fluid side of the piston. The hydraulic pressure of the workingfluid must be high enough to overcome the starting torque (static friction)of the piston. When the pressure exceeds this point, the piston movesoutward, compressing the pneumatic spring. After a predetermined timeperiod, cooling water is sent through the heat exchanger. As thetemperature decreases, the volume of the working fluid shrinks. Thebackpressure of the pneumatic spring helps push the piston back to itsstarting position.

Multiple piston engines have been built and operated. In two pistonapplications, the two pistons can be configured so that they offset eachother in a single cylinder. As one piston extends, the other retracts.Between the pistons are two working chambers that allow the engine to dowork, such as compressing gas, pressurizing water, or pumping hydraulicfluid through a hydraulic motor to turn a shaft. In four piston applications,heat exchanger assemblies timed to run at staggered intervals are utilizedon each of the four cylinders. Valves that direct either the heated water orthe cooling water to flow through the heat exchanger are timed using the


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four pistons. The four cylinders work in sequence continuously applyingpower to turn a rotating shaft for varying applications.

Development of the revolutionary NE Engine technology began in 1984,with the first working model that ran off hot and cold water from Brian

Hagemans kitchen sink in Phoenix, Arizona. Brian continued to build onthis idea, developing and refining the technology. Exhibit A shows keymilestones in the development of the NE Engine, and initial commercialapplication of the technology.

Sources of Efficiency and Economy

The fundamental design of the engine provides the basis for its efficiencyand economy. First, the engine has an inherent efficiency because so littleenergy is dissipated in heat loss and noise generation. In an internalcombustion engine, for example, much of the BTU energy in the gasoline

is sent out the tailpipe as waste heat, but the NE Engine can actuallyrecycle whatever heat is not used. In part, this is because the engineoperates at low temperatures the NE Engine uses heat differentials ofapproximately 100 Fahrenheit to produce usable power.

Additionally, the NE Engine is more efficient because so little energy isused for indirect motions. An internal combustion engine uses asignificant fraction of its power to overcome friction and operate ancillaryfunctions, such as valves, cooling circulation, and the like. Additionally,each cylinder in an internal combustion engine typically provides poweronly on every second or fourth stroke, while each stroke of the NE Engine

is a power stroke.

Another efficiency advantage of the engine is in power transfer. Unlike aninternal combustion engine, for example, there are no camshafts with theirfriction and power losses, no gearing, and no transmission. Of course, inapplications where linear power must be converted to rotary power,traditional methods or even hydraulic converters can be used. Althoughthe engines high torque typically makes gearing and transmissionsunnecessary, gearing is one option to generate even more rapid or slower movement than the engines normal cycle.

The result is a highly efficient, virtually silent, direct drive engine that caneasily be configured to use no traditional fuels and generate no pollutionwhatsoever.

In sum, the real economic advantage of the NE Engine is its loweroperating cost and increased efficiency over competing gasoline, diesel orelectric powered engines. Unlike conventional engines that require costlyfossil fuel or electricity, the NE Engine fuel is simply low grade heat


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something that can be supplied by a variety of sources including solarthermal, geothermal, ocean thermal, waste heat or small amounts ofelectricity or carbon-based fuels. The engines ability to effectively utilizelow grade heat results in minimal fuel costs.

The NE Engine is inherently simple with few moving parts; therefore, iseasier to manufacture and to maintain than conventional engines. Delugestechnology creates an affordable alternative to the more technologicallycomplex products currently available.

Product Features and Benefits

Unlike photovoltaics and fuel cells, technologies that are inherentlycomplex and expensive to manufacture, the NE Engine is relativelysimple, utilizing components similar to those found in traditional internalcombustion engines. As a result, production units can be sold at a price

that provides customers an attractive investment payback period.

Although the technology application is new to the commercialmarketplace, the underlying technology is soundly established. Deluge hasplaced an emphasis on off-the-shelf component materials with the resultthat production of the engines will not require complex manufacturingequipment or facilities, or large capital investment in new plants.

In addition, the technology is a mechanical hydraulic engine of robustdesign. The product life, when properly maintained, is estimated to beapproximately 50 years. Product warranty calculations are based on a 20

30 year life span. This allows maximization of the return on investment.Additional financial benefits include paying for capital costs of purchasedequipment in a relatively short period of time and extending the profitablelife of leased equipment by practicing good preventive maintenance.

Overall features and benefits of NE Engine technology include thefollowing:

* Proven Technology: The engine is based on recognized, proven,understandable technology of modest complexity.

* Flexible Design: The engine is designed so that it can be fabricatedusing existing off-the-shelf components and machined parts from existingfabrication plants, enabling access to a diverse source of parts vendorsaround the world, resulting in competitive pricing.

* Simple Maintenance: Training is of a mechanical nature, and doesnot require expensive high tech testing equipment, allowing for a broad


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range of skilled individuals who can be made field ready in a relativelyshort period of time.

* Durability: The engine has a robust design for long functional life,and easy repair and maintenance.

* Independent Power: Self-contained products can easily be configuredthat work well off the grid in remote locations.

* Multiple Fuel Options: Multiple fuel sources include solar thermal,geothermal, ocean thermal, natural gas, propane, waste heat and others,allowing for flexibility in choosing the most cost effective and availableenergy and backup energy source options.

* Low capital cost: The Company projects that engine configurationscan easily be priced at some 60-85% of power systems that produce

equivalent output.

* Low operating costs: Depending on configurations, operating costscan easily range from 25-75% of power systems that produce equivalentoutput, and can actually be as little as 4% (a 96% reduction in costs) which can justify replacement due to the quick payback.

* Pollution free: The engines create no environmental waste, areinherently safe to operate, and produce no noise. They can be configuredto be entirely green and pollution free.

* Cost Efficiencies with Size: As engines are built in larger sizes, adramatic decrease in cost will occur when approaching the 200horsepower range. As with many technologies, projections beyond thatrange will continue to reduce the cost per horsepower.

Alternative energy and green technology applications are also a benefit.Since the heat input required is low compared to other engines, and theheat differential required to cycle the engine is not large, the engine isenvironmentally friendly. When configured in conjunction with sometraditional technologies, it can actually reduce overall heat emissions. It isexceptionally well suited to green applications, where it can improve the

work outputs from traditional green technologies.

Independent Analysis of the Natural Energy Engine

Verification of the NE Engines capabilities has been documented invarious forms. Third party discovery, experimental and empiricalevidence, and documentation important for acceptance by the generalpublic, the engineering world, and financial institutions are available.


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In fact, the NE Engine and the basic engine technology have benefitedfrom a substantial amount of third party examination and endorsement,including the implicit endorsement provided by the patent awards. Fiveexamples of independent verification follow:

In 1998, an earlier version of the NE Engine was tested at SandiaNational Laboratories in New Mexico. Through a facilities use agreement,the engine was connected to an engine dynamometer system at Sandiassolar research center. Data was collected by Sandia and delivered to alocal Phoenix engineering company for evaluation. The engineering reportprovided the first documented proof that the engine produced horsepower.

In 2001, a Masters thesis was written by David Jacobi, a graduateengineering student under the guidance of Dr. Patrick Phelan, a professorin the Mechanical & Aerospace Engineering Department at Arizona StateUniversity. This thesis provided an in-depth analysis of the physics of the

NE Engine, and described and documented the engines operation in termsof engineering and physics equations. The thesis also provided insights foradvancing the design of the engine to improve performance.

In 2001, testing of a water pump system, using the NE Engine, wasconducted at the Indian Institute of Technology in Chennai, India. Anextensive review was held at the laboratory where over 200 tests wereperformed and documented. The resulting study report provided valuabletemperature/pressure cycle data used to determine the repeatability ofcycling and sequencing of the engine timing.

In 2003, Deluge entered into a Cooperative Research andDevelopment Agreement with the U.S. Department of Energy at theRocky Mountain Oil Testing Center (RMOTC) in Wyoming. Testing ofthe first commercial application of a single cylinder NE Engine wasperformed by a pump designed and built for lifting crude oil fromunderground formations. Various components of the prototype weretested. The actual field testing on an existing oil well at RMOTC providedvaluable development knowledge and earned Deluge the FederalLaboratories Consortiums Outstanding Technology Development Awardin 2005. See Exhibit B.

In 2004, Deluge entered into a Cooperative Research andDevelopment Agreement with the U.S. Department of the Interior at theWater Quality Improvement Center in Yuma, Arizona. A bench test wasperformed using the engine to pressurize salt water processed through areverse osmosis membrane to produce drinking water. The successful testswere monitored by a computer logging instrument and compiled into anavailable report. This same process can be used to purify produced oil wellwater.


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In 2006, Deluge engaged the independent engineering firm of ESGEngineering, based in Tempe, Arizona, to conduct an independent analysisof the comparative efficiency, both physical and economic, of the NEEngine in oilfield use. Their analysis indicates that NE Engine electricalcosts can be less than one-twenty-fifth of the costs of traditional pumping.

Depending on field conditions and pump alternatives, NE Engineoperating costs range from 3.5% to 15% of typical costs. See Exhibit C.

Deluge has benefited from relationships with university professors inArizona, some of whom have consulted on engineering matters. ProfessorPhelan, who has been working with the NE Engine development team forabout seven years, is the primary contact at Arizona State University.While Mr. Jacobi was writing his Masters thesis on the NE Engine, ASUhelped devise a computer modeling program to assist in developing largerengines. The development team is presently working with ASU onadditional projects surrounding the core fundamentals of NE Engine

technology that will lead to further commercial application.

Intellectual Property

As with any such fundamental innovation, patent protection is critical.Accordingly, Deluge has sought and obtained excellent patentprotection on the NE Engine design. Patents for the engine have beenissued in 39 industrialized countries around the world and are pending inthree others. Details of the patent application and award status appear inExhibit D.

The patented name of the engine is a hydraulic engine powered byintroduction and removal of heat from a working fluid. The preparationof patents was expensive and time consuming, and the decision on whereto apply for patents was thoughtfully made. In the United States, twopatents have been obtained, the second being an extension and elaborationof the first.

The Company fully expects that it will seek and obtain additional patentsas the manufacturing process matures, as refinements are made to theapplication of the engine to various uses, and as modifications andextensions are made to the technology. This is considered by Companymanagement to be a critical element in extending the competitiveadvantage of the engine.

To date, funding for all R&D, design, testing, and other technologyprojects has been accomplished through private investors who purchasedcommon stock in Deluge, Inc.


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THERMAL HYDRAULIC ENGINEHAGEMAN BRIAN CSI0920572T - 2006-06-30

THERMAL HYDRAULIC ENGINE

Inventor: HAGEMAN BRIAN CWO98079621998-02-26

Hydraulic engine powered by introduction and removal of heat from aworking fluidInventor: HAGEMAN BRIAN CEC: F01B29/10; F01K25/02 IPC: F01B29/10; F01K25/02; F01B29/00US5916140 - 1999-06-29

US Patent # 5,916,140

Brian Hageman

June 29, 1999

Hydraulic Engine Powered by Introduction and Removal of

Heat from a Working Fluid


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Abstract ---

A thermal hydraulic engine including a frame. A working fluid changesvolume with changes in temperature. A working fluid container houses theworking fluid. A cylinder secured to the frame includes an interior space.

The cylinder also includes a passage for introducing the working fluid intothe interior space. A piston is housed within the interior space of thecylinder. The working fluid container, the interior space of the cylinder,the piston, and the working fluid container define a closed space filled bythe working fluid. The engine also includes means for transmitting heat toand removing heat from the working fluid, thereby alternately causing theworking fluid to expand and contract without undergoing a phase change.The piston moves in response to the expansion and contraction of theworking fluid.

Current U.S. Class: 60/525 ; 60/530

Current International Class: F01B 29/00 (20060101); F01B 29/10(20060101); F01K 25/00 (20060101); F01K 25/02 (20060101); F01B

029/10 ()

References CitedU.S. Patent Documents

2963853 December 1960 Westcott, Jr.3055170 September 1962 Westcott, Jr.3183672 May 1965 Morgan3434351 March 1969 Poitras

3984985 October 1976 Lapeyre3998056 December 1976 Clark4027480 June 1977 Rhodes4107928 August 1978 Kelly et al.4283915 August 1981 McConnell et al.4375152 March 1983 Barto4441318 April 1984 Theckston4452047 June 1984 Hunt et al.4458488 July 1984 Negishi4488403 December 1984 Barto4509329 April 1985 Breston4530208 July 1985 Sato4553394 November 1985 Weinert4637211 January 1987 White et al.4747271 May 1988 Fischer5025627 June 1991 Schneider5195321 March 1993 Howard

Foreign Patent Documents


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32 32 497 Feb., 1983 DE

Description

FIELD OF THE INVENTION

The invention relates to an engine that is powered by the expansion andcontraction of a working fluid as heat is alternately applied to andremoved from the working fluid.

BACKGROUND OF THE INVENTION

Typically, energy is not in readily utilizable forms. Many means exist forconverting one type of energy to another. For example, an internalcombustion engine can turn the explosive force of a fuel burned in itscylinders into mechanical energy that eventually turns the wheels of a

vehicle to propel a vehicle. An internal combustion engine channelsenergy resulting from the burning of a fuel in a cylinder into a piston.Without the cylinder and piston, the energy resulting from the burning ofthe gas would simply spread out in every available direction. Anotherexample of a device to convert one form of energy into another is awindmill. If connected to an electric generator, windmills can convert themechanical action of moving air into electricity.

While an internal combustion engine typically produces mechanicalenergy from the burning of fossil fuels, such as gasoline, diesel fuel, ornatural gas or alcohols, other attempts have been made to produce

mechanical energy from the movement of members such as pistons bymeans other than the burning of fossils fuels. However, most of thesedevices still operate on the basic principle of providing a force to drive amoveable member such as a piston. The difference among the variousdevices in the way in which the force is produced to move the piston andthe way in which the force is controlled.

Some of these devices utilize the movement of a working fluid to drive amoveable member, such as a piston. Other devices utilize the phasechange in a liquid to drive a moveable member. In their operation, somedevices 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 constantlyfocuses on ways to produce energy or power the devices that we rely on inour daily lives. In recent years, another area of research has includedalternative sources of energy. Such research has constantly increased.Among the reasons for the increased research is an increased awareness ofthe limited amount of fossil fuels in the earth. This research may also be


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spawned by an increased desire to provide energy for people living inremote locations around the world who now live without power.

Among the alternative sources of energy on which research has beenfocused is solar energy. Solar energy has been captured by photovoltaic

cells that convert the sun's energy directly into electricity. Solar energyresearch is also focused on devices that capture the sun's heat for use in avariety of ways.

As discussed above, in relation to the internal combustion engines andwindmill examples, the problem being addressed both by photovoltaicsolar cells and solar heating devices is the conversion of one type ofenergy to another type of energy. In solar cells, the energy in sunlight isused to excite electrons in the solar cells, thereby converting the sun'senergy to electrical energy. On the other hand, in solar heating cells, theenergy 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 problemsin mind. As a result, the present invention is directed to a new device forconverting one form of energy to another. The present invention may alsoutilize solar or other unconventional forms and/or sources of energy.

Accordingly, the present invention provides a thermal hydraulic enginethat utilizes the expansion and contraction of a fluid by alternately

transmitting heat to and removing heat from an operating fluid. Theenergy may provide mechanical and/or electrical energy.

One advantage of the present invention is that it may utilize a variety ofsources of heat to heat and/or cool the working fluid.

Consequently, another advantage of the present invention is that it issubstantially non-polluting.

Along these lines, an additional advantage of the present invention is thatit may run off heat energy and, therefore, may be solar powered.

Furthermore, an advantage of the present invention is that, since it may besolar powered, it may be utilized to provide power in remote areas.

An additional advantage of the present invention is that it may utilize heatand/or heated water produced by existing processes. Accordingly, thepresent invention may make use of heat energy that is otherwise currentlynot utilized and discarded as waste.


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A still further advantage of the present invention is that it may operatewithout using fossil fuels.

It follows that an advantage of the present invention is that it may produceenergy 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 arelatively simple design that eliminates the need for a complex series ofvalves to control the flow of a working fluid through the system.

Accordingly, a further advantage of the present invention is that itprovides a simple design, thus reducing construction and maintenancecosts.

In accordance with these and other objectives and advantages, the present

invention provides a thermal hydraulic engine. The engine includes aframe. The engine utilizes a working fluid that changes volume withchanges in temperature. A working fluid container houses the workingfluid. A cylinder is secured to the frame and includes an interior space.The cylinder also includes a passage for introducing the working fluid intothe interior space. A piston is housed with the interior space of thecylinder. The working fluid container, the interior space of the cylinder,the piston, and the working fluid container define a closed space filled bythe working fluid. The engine also includes means for transmitting heat toand removing heat from the working fluid, thereby alternately causing theworking fluid to expand and contract without undergoing a phase change.

The piston moves in response to the expansion and contraction of theworking fluid.

According to additional preferred aspects, the present invention provides athermal hydraulic engine. The engine includes a frame. The engine alsoincludes a working fluid that changes volume with changes intemperature. A working fluid container houses the working fluid. Aflexible diaphragm is provided at one end of the working fluid container.The flexible diaphragm moves in response to expansion and contraction ofthe working fluid without a phase change in the working fluid. Aconnecting rod in contact with the flexible diaphragm moves in responseto movement of the flexible diaphragm. The engine also includes meansfor transmitting heat to and removing heat from the working fluid, therebyalternately causing the working fluid to expand and contract.

Still other objects and advantages of the present invention will becomereadily apparent by those skilled in the art from the following detaileddescription, wherein it is shown and described only the preferredembodiments of the invention, simply by way of illustration of the best


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mode contemplated of carrying out the invention. As will be realized, theinvention is capable of other and different embodiments, and its severaldetails are capable of modifications in various obvious respects, withoutdeparting from the invention. Accordingly, the drawings and descriptionare to be regarded as illustrative in nature and not as restrictive.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 represents a schematic diagram illustrating an embodiment of apower plant including a thermal hydraulic engine according to the presentinvention;

FIG. 2 represents a schematic diagram illustrating various components ofan embodiment of a solar powered thermal hydraulic engine according tothe present invention;


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FIG. 3 represents an overhead view of various components that may bedriven by a thermal hydraulic engine according to the present invention,representing the "load" on the engine;

FIG. 3a represents an embodiment of a chain drive gear and sprocket thatmay be driven by a thermal hydraulic engine according to the presentinvention;


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FIG. 4 represents a schematic diagram illustrating various components ofanother embodiment of a solar powered thermal hydraulic engineaccording to the present invention utilized to drive a water pump;

FIG. 5 represents an embodiment of a thermal hydraulic engine accordingto the present invention including three cylinders;


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FIG. 6 represents the various stages of the operation of an embodiment of

a thermal hydraulic engine according to the present invention that includesthree cylinders;


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FIG. 7 represents an embodiment and operation of a thermal hydraulicengine according to the present invention that includes four cylinders;


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FIG. 8 represents the position of a piston at the beginning of a powerstroke of a piston of an embodiment of a thermal hydraulic engineaccording to the invention;

FIG. 9 represents the rotational location of a crank shaft in a thermalhydraulic engine according to the present invention, indicating the variouspositions of the crank shaft relative to the expansion and contraction of theworking fluid and introduction and removal of heat from the workingfluid;


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FIG. 10 represents a graph showing operating ranges of temperatures andpressures of a working fluid utilized in an embodiment of a thermalhydraulic engine according to the present invention;


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FIG. 11 represents a cross-sectional view of an embodiment of a heatexchanger for use with a thermal hydraulic engine according to the presentinvention;

FIG. 12 represents a cross-sectional view of an embodiment of a heatexchanger and working fluid container for use with a thermal hydraulic


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engine according to the present invention that employs mercury as aworking fluid;

FIG. 13 represents an embodiment of a containment wall for use with anembodiment of a working fluid container according to an embodiment ofthe present invention;

FIG. 14 represents a cross-sectional view of another embodiment of acylinder and piston that may be employed in a thermal hydraulic engineaccording to the present invention;


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FIG. 14a represents a cross-sectional view of the embodiment of a pistonand connecting rod shown in FIG. 14;

FIG. 14b represents a cross-sectional view of an embodiment of acylinder and piston, wherein the piston includes a connecting rod attachedto both ends;


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FIG. 15 represents a close-up cross-sectional view of a portion of theembodiment of a cylinder and piston shown in FIG. 14;

FIG. 16 represents a cross-sectional view of an embodiment of an end of acylinder of an embodiment of a thermal hydraulic engine according to thepresent 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.


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FIG. 17 represents a side view of an embodiment of a thermal hydraulicengine according to the present invention that includes a cylinder mountedto a crankshaft and pivotably mounted to a floating anchor sliding within aguide mounted to a frame;

FIG. 18 represents the embodiment shown in FIG. 17, wherein the pistonis starting its power stroke and the crankshaft has started to rotate;


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FIG. 19 represents the embodiment shown in FIGS. 17 and 18, whereinthe piston has started its return stroke and the floating anchor is slidingback into its guide;

FIG. 20 represents a side view of an embodiment of a thermal hydraulicengine according to the present invention that includes two springs for

biasing the piston in the direction of its return stroke and a floating anchorshown in FIGS. 17-19;

FIG. 21 represents a side view of an embodiment of a thermal hydraulicengine according to the present invention that includes a frame thatcomponents of the engine are mounted on;


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FIG. 22 represents a cross-sectional view of an embodiment of a cylinderof a thermal hydraulic engine according to the present invention in whicha heat exchanger is mounted within the working fluid container;

FIGS. 23A-23H represent cross-sectional views of an embodiment of athermal hydraulic engine according to the present invention that includesfour cylinders radially arranged, illustrating the engine throughout variousportions of a cycle of the engine;


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FIG. 24 represents a perspective view of the embodiment shown in FIGS.23A-23H;

FIG. 25 represents an embodiment of a cylinder that may be included in a

thermal hydraulic engine according to the present invention wherein thecylinder includes a single inlet and outlet port for passage of a workingfluid into and out of the cylinder;

FIG. 26 represents an embodiment of a cylinder that may be included in athermal hydraulic engine according to the present invention wherein thecylinder includes two ports for passage of hydraulic fluid into and out ofthe cylinder, such that the return stroke of the piston is also a poweredstroke;


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FIG. 27 represents a schematic view of an embodiment of a thermalhydraulic engine according to the present invention that includes directthermal exchangers rather than heat exchangers for introducing heat intothe working fluid of the thermal hydraulic engine;

FIG. 28 represents a cross-sectional view of an embodiment of a directthermal exchanger that may be utilized in an embodiment of the inventionshown in FIG. 26;


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FIG. 29 represents an end view of the direct thermal exchanger shown inFIG. 28;

FIG. 30 represents a close-up end view of the direct thermal exchangershown in FIGS. 28 and 29;

FIG. 31 represents a cross-sectional view of an embodiment of amechanical valve that may be utilized to direct working fluid and/orheating fluid and/or cooling fluid to various parts of a thermal hydraulicengine according to the present invention;


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FIG. 32 represents a cross-sectional view of an embodiment of acrankshaft and a piston crank arm that may be included in a thermalhydraulic 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 aportion of the cycle of the engine;


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FIG. 34 represents a cross-sectional view of a cylinder of a thermalhydraulic engine according to one embodiment of the present inventionthat includes a crankshaft shown in FIG. 31-FIG. 33, illustrating theposition of the piston crank arm throughout a portion of the cycle of theengine;


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FIG. 35 shows a cross-sectional view of another embodiment of acrankshaft and piston crank arm arrangement that may be utilized in athermal hydraulic engine according to the present invention;

FIG. 36 represents a side view of a crank moment arm that includesstiffening ribs;


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FIG. 37 represents another embodiment of a thermal hydraulic engineaccording to the present invention and various associated componentsincluding a solar heat collector;

FIG. 38 represents an overhead view of the solar heat collector shown inFIG. 37;


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FIG. 39 represents a cross-sectional side view of a solar heat collectoraccording to the present invention including a seasonal tracking chaindrive and counterweight showing various positions of the solar heatcollector;

FIG. 40 represents a further alternative embodiment of a thermalhydraulic engine according to the present invention;


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FIG. 41 represents a still further alternative embodiment of a thermalhydraulic engine according to the present invention;


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FIG. 42 represents an embodiment of a transmission that includes aflywheel that may be used with an embodiment of a thermal hydraulicengine according to the present invention;


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FIG. 43 represents an embodiment of a thermal hydraulic engineaccording to the present invention that includes a piston that is poweredboth on its power stroke and its return stroke, includes a passive solar heatcollector as a heat source, and powers a water pump; and


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FIG. 44 represents a further embodiment of a cylinder, piston and crankarm according to the present invention.


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DETAILED DESCRIPTION OF VARIOUS AND PREFERRED

EMBODIMENTS OF THE INVENTION

As stated above, the present invention is an engine that derives powerfrom the expansion and contraction of a working fluid as heat is

alternately applied to and removed from the working fluid. The expansionand contraction of the fluid is transformed into mechanical energy, via thepresent invention. The mechanical energy may be utilized directly.Alternatively, the mechanical engine may be turned into another form ofenergy, such as electricity.

Accordingly, the present invention includes a working fluid thatexperiences changes in volume with changes in temperature. Any suchfluid may be utilized in a thermal hydraulic engine according to thepresent invention. However, more power may be realized from theoperation of the engine if the working fluid experiences greater changes in

volume over a range of temperatures than fluids that experience lesserchanges in volume over the same temperature range.

The present invention operates at least in part on the principle that fluidsare generally not compressible. Therefore, according to the presentinvention, the working fluid does not change form into another state, suchas a solid or a gas during the operation of the engine. However, any fluidthat undergoes an expansion or contraction with a change in temperaturemay 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 atwhich heat is transferred to the fluid. For example, if a fluid quicklychanges temperature, the speed of the engine may be faster. However, insome cases, a fluid that quickly responds to changes in temperature mayhave a low coefficient of expansion. Therefore, these factors mustbalanced in order to achieve the desired effect for the engine. Other factorsthat may be considered in selecting a working fluid include any causticeffects that the fluid may have on the working fluid container, theenvironment, and/or people working with the engine.

A very important factor in determining the size, design, cost, speed, andother characteristics of a thermal hydraulic engine according to the presentinvention is the working fluid. Various fluids have various thermalconductivities and coefficients of expansion, among other characteristics,that may effect the characteristics of the engine. For example, thecoefficients of expansion of the working fluid may determine the amountof working fluid necessary to operate the engine. The coefficient ofexpansion may also effect the amount of heat necessary to expand theworking fluid.


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Changing the amount of heat necessary to expand the working fluid maychange the size of a solar heat collector providing heat, the size of a heatexchanger imparting heat, among other factors. In embodiments of thepresent invention in which heat is provided by other sources of energy, theamount of energy necessary to generate heat to expand the working fluid

may be altered based upon the thermal expansion characteristics. Forexample, if a fluid expands to a high degree as heat is imparted to it, lessheat will be required to provide the necessary expansion for the engine.This permits a decrease in the size of solar collectors, a decrease in theamount of energy necessary to expand the fluid or a decrease in the size ofthe heat exchanger, for example.

FIG. 27 shows an example of a thermal hydraulic engine that includes asolar heat source. Although the embodiment shown in FIG. 27 includessolar heat collectors, a variety of heat sources may be utilized, whether thedirect heat transfer or heat exchangers are utilized. For example, a thermal

hydraulic engine according to the present invention may utilize low gradeheat to perform work. A thermal hydraulic engine according to the presentinvention 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 toimpart heat to the working fluid of the present invention when utilizingany of the above-discussed fuels.

An example of a working fluid that may be utilized according to thepresent invention is water. Another fluid that may be utilized is mercury.

Additionally, other substances that may be utilized as a working fluidinclude FREON, synthetic FREONS, FREON R12, FREON R23, andliquified gasses, such as liquid argon, liquid nitrogen, liquid oxygen, forexample. FREON and related substances, such as synthetic FREONS,FREON R12, and FREON R23, may be particularly useful as a workingfluid due to the large degree of expansion that they may undergo as heat isintroduced into them and the tendency to return to their original volumeand temperature upon removal of heat. Another example of a workingfluid that may be utilized according to the present invention is liquidcarbon dioxide. Other fluids that may be utilized as working fluids includeethane, ethylene, liquid hydrogen, liquid oxygen, liquid helium, liquifiednatural gas, and other liquified gases. Other working fluids may also beused, as one skilled in the art could determine without undueexperimentation once aware of this disclosure.

In order to capture the energy in the expansion of the fluid, the workingfluid is housed within a closed space. The closed space may include manydifferent elements. However, the closed space typically includes at least aworking fluid container.


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Preferably, the working fluid entirely fills or substantially entirely fills theinterior 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 denseststate, wherein it occupies the least amount of volume. The working fluid

container may then be sealed or connected to other components of theengine.

The volume of the working fluid container depends upon, among otherfactors, the size of the engine, the application, the amount of working fluidrequired for the application, the amount that the working fluid expandsand contracts with changes in temperature. The exact interior volume ofthe working fluid container will be discussed below in relation to specificembodiments. However, such embodiments are only illustrative in natureand not exhaustive and, therefore, only represent examples of workingfluid containers.

Preferably, the working fluid container is made of a material that canwithstand the pressure from the working fluid as the working fluidexpands. Materials that may be utilized to form the working fluidcontainer include metals, such as copper, plastics, ceramics, carbon steel,stainless steel or any other suitable materials that may withstand thetemperatures and pressures involved in the specific application.Regardless of the material used, preferably, it is non-deformable orsubstantially so when subjected to the forces generated by the expansionof the fluid. The material may change due to the effect of heat butpreferably not due to the force from the expanding fluid. The non-

deformability of the material that working fluid container is made ishelpful for transmitting the force of the expansion of the working fluid towhatever moveable member, such as a piston, the particular embodimentof the present invention includes.

Another stress that the working fluid container is subjected to results fromthe heating and cooling of the working fluid. As the temperature of theworking fluid increases, the working fluid container may expand, due tothe application of heat. Similarly, as the working fluid cools, the materialsin contact with the fluid will cool and may contract.

Therefore, regardless of the material used, not only should it be capable ofwithstanding temperatures and pressures of a particular application, but itmust also be able to withstand the changes in temperatures and pressuresthat continuously occur during the operation of a thermal hydraulic engineaccording to the present invention. For instance, metal fatigue could be aproblem in embodiments in which are made of metal. However, metalfatigue may be overcome by those skilled in the art who can adapt the


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particular metal to the particular conditions involved in a particularembodiment.

Accordingly, it is preferable that the materials in contact with the workingfluid, such as the working fluid container, also have some elastic

characteristics. A material that is excessively brittle might tend to crackand leak, rendering the engine inoperable.

The number of working fluid containers included an embodiment of thepresent invention typically depends upon the number of cylinders or otherdevices utilized for capturing the energy of the expansion of the workingfluid. Preferably, the number of working fluid containers is equal to thenumber of expansion capturing devices. However, it conceivable that therecould 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 theexpansion of the working fluid. Such an embodiment may include twoworking fluid containers for each cylinder. Therefore, as can beappreciated, the number of working fluid containers in the embodiment ofthe invention may vary.

The working fluid container may be interconnected with a cylinder.Alternatively, the working fluid container may be isolated in a fluidcontainment system. According to such a system, the force generated bythe expansion of the working fluid is not transmitted directly to a piston orother movable member, but is indirectly transmitted.

If the working fluid container and cylinder are connected so that the forceof the expansion of the working fluid is directly transmitted to a piston orother movable member, the working fluid container and cylinder may beinterconnected in a variety of ways. For example, a tube, hose or otherconduit may be utilized to connect the working fluid container with thecylinder. Alternatively, the working fluid container may be directlyconnected to the cylinder. Preferably, if the cylinder is connected to theworking fluid container with a hose or other conduit, the hose or conduit isalso made of a material the resists changes in shape as a result of theforces applied by the expansion of the working fluid. An example of sucha material includes steel reinforced rubber hose.

As stated above, the working fluid may be isolated in the working fluidcontainer. According to such embodiments, rather than being directlytransmitted to the piston, the force of the expanding fluid may betransmitted to a hydraulic fluid, which then transmits the force to thepiston.


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According to such embodiments, the working fluid is housed within theworking fluid container. The working fluid container is in contact with theheat exchanger. However, rather than the working fluid traveling from theworking fluid container into a cylinder to actuate a piston as the fluidexpands, 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 FIG. 12, the working fluid container and thehydraulic system may be thought as defining two sections making up anoverall fluid containment system. The flexible blind flange 180 may bethought of as isolating the working fluid. Therefore, the working fluidcontainer 182 in such embodiments may be referred to as a fluid isolationsection. Another part of the fluid containment system is the hydraulicsystem 184. The hydraulic system may be thought of as a transfer sectionthat transfers the force of the working fluid to the piston.

A fluid containment system is particularly useful if the working fluid is acaustic or hazardous material, such as mercury. Not only does thecontainment and transfer section permit a hazardous working fluid to beused with the engine, but it also permits the sections of the engine to bemanufactured and shipped separately and be maintained separately. Forexample, the working fluid container, with or without the heat exchanger186, could be shipped separately from the heat exchanger and cylinder towhich it is be interconnected with.

The fluid containment system includes the flexible blind flange as well asthe hydraulic reservoir and other hoses, fittings, tubing, and passageways

that may be necessary to permit the hydraulic fluid to operate the piston.As discussed above, the flexible blind flange permits the force of theexpanding wording fluid to be transmitted to the hydraulic fluid.Regardless of the components and materials utilized in constructing thefluid containment system, preferably it maintains the temperature andpressure of the working fluid.

According to one such embodiment, a mounting flange 188 extends aboutthe opening of the working fluid container 182. Preferably, the flexibleblind flange 180 is then positioned on the mounting flange 188 connectedto the working fluid container 182. The hydraulic fluid reservoir may thenbe attached over the flexible blind flange. Preferably, the hydraulic fluidreservoir preferably includes a mounting flange 190 having a shapecorresponding to the shape of the mounting flange 188 on the workingfluid container 182. The hydraulic fluid reservoir and the working fluidcontainer may then be tightly connected together in order to seal the spacebetween them, thereby preventing the working fluid from escaping theworking fluid container.


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The hydraulic fluid reservoir is connected directly or through one or moreconduits to the cylinder. The hydraulic fluid then acts as the working fluidother wise would if it were not isolated in the working fluid container.According to such an embodiment, as the working fluid expands, it appliespressure to the flexible blind flange. The flexible blind flange then applies

force to the hydraulic fluid. A pressure is then created on the hydraulicfluid. The pressure applied to the hydraulic fluid, causes it to placepressure on all surface of the reservoir, cylinder, and piston. Since thepiston is the only movable member in the system, it moves in response tothe pressure.

FIG. 13 shows the containment wall between the interior of the workingfluid container and the interior of the heat exchanger.

The number of working fluid containers and possibly containment sectionsmay vary, depending upon, among other factors, the number of cylinders

and whether a power return stroke, as described below, is utilized.

As discussed above, the working fluid expands and, either directly orindirectly, the expanding fluid is directed to a cylinder. The cylinder is atthe heart of the invention since the cylinder houses the piston that theforce of the expanding working fluid is transmitted to, thereby moving thecylinder and initiating the mechanical energy produced by the invention.

As with the working fluid container and other components of theinvention, the cylinder may be made of a variety of materials. The abovediscussion regarding stresses on the working fluid container and the

material that it is made of applies to the cylinder. Accordingly, the samematerials may be utilized to form the cylinder.

The size of the cylinder may vary, depending upon a number of factorsrelated to the specific application. Factors that may be important isdetermining the size of the cylinder include, among others, the number ofcylinders, the particular load on the engine, and the amount of power to beproduced. A typical size of the maximum interior volume of a cylinderincluded in a thermal hydraulic engine according to the present inventionis from about 350 cubic inches to about 20,000 cubic inches. However, thesize of each of the cylinders may vary from about 4 inches in diameter toabout 36 inches in diameter.

According to one embodiment, an engine with a cylinder having adiameter of about 5 inches and a piston stroke of about 18 inchesgenerates about 10 horsepower.

Preferably, the cylinder has a circular or substantially circular crosssectional shape.


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FIGS. 5, 7, and 14 illustrate examples of various embodiments ofcylinders that may be utilized in a thermal hydraulic engine according tothe present invention.

The cylinder may be mounted to a frame upon which other components of

the present invention may be mounted. The cylinder may be fixably orarticulately mounted to the frame. FIGS. 17, 18, and 19 show anembodiment of the present invention in which the cylinder 200 isarticulately or pivotably mounted to a frame 202. According to thisembodiment, the cylinder 200 includes a connecting member 204, such asa fork or other suitable member, that may be pivotably joined to acomplementary member on the frame 202. A pin 206 is one means forconnecting the cylinder to the frame that may be utilized.. As the pistonmoves through its cycle, and the crankshaft rotates, the cylinder will pivotabout its anchor.

The embodiment shown in FIGS. 17-19 also includes a floating anchor.According to this embodiment, the cylinder is pivotably mounted to theanchor to that the cylinder can pivot. The anchor is movably mountedwithin a guide 208. The guide 208 permits the anchor to slide from right toleft as shown in FIGS. 17-19. The guide 208 may be directly or indirectlyconnected to the frame 202.

The floating anchor permits the piston to contract without having to waitfor the crankshaft to continue its rotation and without having to overcomeany other forces tending acting on the piston in a direction opposite to itsreturn stroke.

Regardless of the embodiment of the present invention, it may include afloating anchor.

FIG. 20 shows an embodiment of a thermal hydraulic engine according tothe present invention that includes springs 210 that bias or tend to movethe piston in the direction of its return stroke. If the engine includessprings, it may include at least one spring. Use of springs to cause thecylinder to move in the direction of its return stroke may be important tomaintain a pressure on the working fluid at all times. With some workingfluids, this is particularly important, such as with FREON, FREONsubstitutes and analogous compounds.

According to the embodiments shown in FIGS. 5, 6, and 7, the workingfluid is introduced into one end of the cylinder. Therefore, cylindersaccording to these embodiments include a connection only at this end.However, according to other embodiments, discussed below in greaterdetail, the return stroke, as well as the power stroke, is powered by aworking fluid. According to such embodiments, the cylinder may include


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means for introducing a working fluid into both ends of the cylinder. Suchembodiments may also include a seal about a connecting rod attached tothe piston, as described below in greater detail.

The working cylinders of a thermal hydraulic engine according to the

present invention may include a port for passage of working fluid into andout of the cylinder. According to such embodiments, the expansion of theworking fluid powers the piston through its power stroke. Such anembodiment is shown in cross-section in FIG. 25.

In this embodiment, cylinder 326 includes an inlet 328 for introduction ofworking fluid into the cylinder. Expansion of the working fluid appliesforce to wall of the surface area that defines the space 330 into which theworking fluid is introduced. As the working fluid expands, it applies forceto the face 332 of piston 334 located within cylinder 326. Seal 336prevents the fluid from entering the remaining portion of the interior

volume of the cylinder. Force applied to the surface of the piston movesthe piston into an extended position, as shown by 338. The piston may bepowered on its return stroke by forces created by the contraction of thefluid, as well as by forces applied to crank arm 340 by other cylinders in amulti-cylinder engine as they experience their power stroke or by otherforces.

FIG. 26 shows an alternative embodiment of a cylinder according to thepresent invention that includes two ports 344 and 346 for passage of aworking fluid into and out of the cylinder. Including two ports for passageof a working fluid into and out of the cylinder permits the piston to be

powered in both directions of movement. In other words, the pistonconstantly experiences a power stroke regardless of the direction ofmovement of the piston.

Such an embodiment does not require outside forces to cause the cylinderto return. A dual port cylinder also permits one piston to do work in twodirections. Significantly, a dual port cylinder may permit a thermalhydraulic engine according to the present invention to operate with onlyone cylinder.

Another benefit of including dual port hydraulic cylinders in a thermalhydraulic engine according to the present invention is that the size of theengine may be decreased since the cylinder may provide power to operatea load with the cylinders moving in each direction. Although the enginemay be reduced in size, a single cylinder with two ports cannot replacetwo cylinders with a single port since the port on the side of the pistonwhere the piston shaft is mounted applies less force to the piston since thesurface area of the piston is reduced by the area of the shaft.


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An additional added benefit of dual port hydraulic cylinders is that theflow of the working fluid between cylinders may be interconnected.According to such an embodiment, the main port, which would be the portthat fluid flows into to drive the piston in its power stroke in a cylinderthat includes only one port, such as port 344 in the embodiment shown in

FIG. 26, may be connected to a second port, such as the port 346 in theembodiment shown in FIG. 26 of a different cylinder.

An embodiment that includes interconnected cylinders permits a piston tobe pushed by a first cylinder being powered by fluid flowing into the mainport and pulled by fluid exiting the second port on that cylinder.According to such an embodiment, the crankshaft will constantly berotated by force applied by all cylinders as the pistons are constantly beingmoved by working fluid flowing into and out of the first and second portssimultaneously. Such a design permits the size of the engine to bedecreased. According to one embodiment, a thermal hydraulic engine

including two ports per cylinder may be decreased by almost one-half size,compared to an engine that includes single port cylinders.

The effect of a dual port cylinder may be at least partially achievedutilizing a single port cylinder if a gas is provided on the side of the pistonopposite the working fluid. The gas may be pressurized to maintainequilibrium of pressures on the piston when the piston is in a fullywithdrawn position. As the piston moves on its power stroke, the gas willbe compressed as the working fluid pushes against the piston. The greaterhydraulic force of the working fluid will typically be much greater thanthe pneumatic force provided by the gas. Therefore, the gas typically will

only slightly restrict the forward motion of the piston. As the workingfluid contracts, the hydraulic forces on the piston are reduced. The reducedhydraulic forces typically are close in magnitude to the pneumatic forcesgenerated by the gas, thereby permitting the gas to help the piston return tothe starting position.

The design of a chamber, utilizing a gas as described above as a spring,maybe designed to avoid developing extreme pressures. The gas pressureshould be higher than the hydraulic pressure at the equilibrium position.Additionally, the gas pressure should be great enough to overcome theinertia of the piston and the frictional forces of the O-ring seal between thepiston and the cylinder wall.

As stated above, a thermal hydraulic engine according to the presentinvention may include only one cylinder. The single cylinder may bepower by fluid flowing into and out of two ports included in the vicinity ofopposite ends of the cylinder. A single cylinder from a hydraulic engineaccording to the present invention may also include at least one flywheelattached to the transmission system to permit full rotation of a crankshaft.


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FIG. 42 shows an embodiment of a transmission that may be utilized witha thermal hydraulic engine according to the present invention. Thetransmission shown in FIG. 42 includes a plurality of gears 800 to gear upthe power created by the engine. The flywheel 802 is on the higher RPMside of the gear up of the transmission. The center shaft 804 is the main

crankshaft of the engine, typically operating at a low rate of revolution.The gears are mounted on 6 inch by 0.5 inch steel plates 806. Also, in theembodiment shown in FIG. 42, the gears are mounted about 16 inchesapart. Of course, one skilled in the art could utilize a different number ofgears mounted in a different manner on different supports. One skilled inthe art could also connect the gears together and to the engine in adifferent manner.

Actually, theoretically, a thermal hydraulic engine according to the presentinvention could include a single cylinder that only includes a single portfor introduction of a working fluid if a flywheel of a size sufficient to

permit rotation of the crankshaft is provided. One skilled in the art coulddetermine the size of the flywheel necessary without undueexperimentation based upon the disclosure contained herein.

A displacable member piston may be located within the cylinder. Oneexample of such a displacable member is a piston. The displacablemember will slide back and forth along the length of the cylinder inresponse to changes in the volume of the fluid with changes intemperature.

In order to maintain the working fluid in a closed space, preferably, the

working fluid is prevented from passing between the cylinder and thepiston. This may be accomplished by providing a piston having a cross-sectional area only very slightly less than the cross-sectional area. Also,helping to ensure a seal between the piston and the cylinder is if the pistonhas substantially the same cross sectional shape as the cross sectionalshape of the interior of the cylinder.

Any space between the piston and the cylinder may be further sealed byproviding a seal about the piston. Alternatively, a seal may be located onthe surface of the piston facing the interior of the cylinder about the edgeof the piston. The seal helps to ensure that the space between the pistonand cylinder is sealed. Sealing the space helps to ensure that any energythat may be derived from the expansion of fluid will be transferred to thepiston and not be wasted by fluid leaking between the piston and thecylinder. If fluid were to leak, it could greatly degrade the performance ofthe engine.

FIGS. 14, 14a, and 15 show an alternative embodiment of a piston andcylinder arrangement that may be utilized in an engine according to the


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present invention. According to this invention, the working fluid isintroduced into the cylinder on both sides of the piston 192. Accordingly,the area where the piston and the cylinder wall 194 meet is sealed by seals196 and 198 on both sides of the piston 192.

In order to transmit the force from the piston to a crankshaft or othertransmission member, a connecting rod may be attached to the piston. Inembodiments without a powered return stroke, the connecting rod may beconnected to the side of the piston opposite the side facing the workingfluid, or hydraulic fluid in embodiments including a working fluidcontainment system. In embodiments including a powered return stroke,the connecting rod is still connected to the piston. However, both sides ofthe piston are in contact with the working fluid.

In embodiments that include the powered return stroke, the end of thecylinder that the connecting rod 200 projects from must be sealed by seal

202 to maintain the pressure of the working fluid for the powered returnstroke.

As shown in FIG. 14a, the force of the working fluid on the side of thepiston that is attached to the connecting rod 200 will only be transmitted tothat portion of the piston 192 surrounding the connecting rod. This causesa reduced effective force being delivered to the crank shaft. This reductionin service area of the piston may be compensated for by increasing thecapacity and speed with which heat is transferred to the working fluid.

FIG. 16 shows an alternative embodiment of a thermal hydraulic engine

that includes a flexible blind flange. According to this embodiment, theforce generated, indicated by arrows in FIG. 16, by the expanding workingfluid applies force to the flexible blind flange 204. The flange then actsupon member 206, thereby displacing member 206. Movement of member206 may be guided by guide 207. Member 206 is interconnected with acrankshaft or other drive mechanism (not shown in FIG. 16). The flange204 may be secured between two mounting flanges 208 and 210 similarlyto the embodiment shown in FIG. 12.

Regardless of whether the engine includes a powered return stroke, theconnecting rod may be fixably or movably attached to the piston. If theconnecting rod is fixably attached to the piston, then the cylinderpreferably is articulately mounted to the frame. Regardless of whether theconnecting rod is movably or fixably attached to the piston, the connectingrod may include one or more sections.

The connecting rod may be connected to a crank shaft and othertransmission elements to drive a device or an electric generator. In someembodiments, the cylinder is fixedly attached to a frame and the


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connecting rod articulately attached to the piston and a crank shaft so thatas the piston moves back and forth through its stroke and the crank shaftrotates, the connecting rod will change its position.

As shown in FIGS. 23A-23H and 24, the cylinders of the thermal

hydraulic engine according to the present invention may be arrangedradially. Utilizing a radial arrangement of the cylinders in the thermalhydraulic engine may permit a more immediate transfer of energy fromthe cylinders to the crankshaft and whatever load is being placed on theengine. Additionally, a radial arrangement of the cylinders may provide amore direct path through the mechanical system of the engine for forcesgenerated by the working fluid. Furthermore, back pressure, discussed ingreater detail below, and other internal loads from the piston and/or pistonO-rings may be more directly handled by the power stroke of the enginewith radially arranged cylinders.

An embodiment of a thermal hydraulic engine according to the presentinvention that includes radially arranged cylinders may include anynumber of cylinders. The number of cylinders in an embodiment of thepresent invention that includes a radial arrangement of cylinders may bean even number or an odd number.

The embodiment of the thermal hydraulic engine according to the presentinvention shown in FIGS. 23A-23H and FIG. 24 includes four cylinders300, 302, 304, and 306. The cylinders may be attached to frame 299. Thepistons (not shown) within the cylinders are connected through crank arms308, 310, 312, and 314 to a connecting member 316. To facilitate rotation

of the crankshaft and the connecting member 316, the connection betweenthe crank arms 308, 310, 312, and 314 may be articulately mounted topistons (not shown) located within cylinders 300, 302, 304, and 306 or toconnecting member 316. The connecting member 316 may beinterconnected through connecting member 318 to crankshaft 320.

FIGS. 23A-23H illustrate the various positions of the pistons, connectingarms, connecting members, and crankshaft throughout a revolution of theengine, as the cylinders experience both power and return strokes. In FIG.23A, piston 300 is in its power stroke. Piston 302 is just beginning itspower stroke. Additionally, piston 304 has completed its cooling or returnstroke. On the other hand, piston 306 is in the beginning stages of itscooling, or return, stroke.

In the view shown in FIGS. 23A-23H, the crankshaft is rotating in aclockwise direction. Piston 304 has completed its cooling cycle on itsreturn stroke and is beginning its heating cycle, but has not yet reached itspower stroke range. By saying that the piston has not reached its powerstroke, it is meant that the working fluid has not reached a pressure


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capable of moving the piston at all or more than an insubstantial amountalong its power stroke. In other words, the pressure is not in a range tomove the piston and the piston is not physically in the range of its powerstroke.

FIG. 24 shows a three-dimensional perspective view of the embodiment ofthe thermal hydraulic engine shown in FIGS. 23A-23H. As can be seen inFIG. 24, the cylinders may be mounted to frame members 322, 324. Pistonmounting frame members 322 and 324 typically are mounted to anotherstructure or structures to secure them.

In any embodiment of the present invention, and particularly, in anembodiment that includes a radial arrangement of cylinders, the coolingcycle of any one piston preferably permits shrinking of the working fluidat a rate equal to or faster than the expanding of the working fluid in apiston that is in its power stroke during the return stroke of the piston in

question. If the cooling of the working fluid is not as rapid as the increasein temperature in the working fluid, the working fluid can create a "backpressure" that may restrict the movement of the piston in its power stroke.The back pressure may create an unnecessary load on the engine,hindering the entire operation of the engine. This is particularly the case inan embodiment of an engine according to the present invention thatincludes a radial arrangement of cylinders since the cylinders are typicallyarranged in opposing pairs.

If one cylinder experiences a back pressure as a result of a less rapidcooling and shrinking of the working fluid, as compared to the heating and

expansion of the working fluid, in another cylinder undergoing its powerstroke at the same time, the cylinder undergoing its power stroke will beinhibited in its movement by the back pressure. As such, the back pressureacts as an additional load on the engine in addition to whatever load, suchas a pump or other device that the engine is driving.

One way to help prevent the occurrence of back pressure is to ensure thatheat is removed from the working fluid quickly enough. This may beaccomplished by ensuring a flow of cooling fluid sufficiently rapid toresult in a removal of heat from the working fluid in the cylinderundergoing a return stroke at a rate equal to or greater than thetransmission of heat to the working fluid in the cylinder undergoing apower stroke. If, as describe herein, the engine does not include heatexchangers, then preferably, the rate of heat transfer from the workingfluid in the cylinder undergoing the return stroke is equal to or greater thanthe rate of transmission of heat to the working fluid in the cylinderundergoing the power stroke. Removal and transmission of heat may bedependent upon characteristics of the working fluid, the cooling sourcematerial, the heat exchanger, among other factors.


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The transmission elements are then connected to a load to perform adesired function. For example, the engine could power a water pump, anelectric generator, and/or a FREON compressor, among other elements.

In order to transmit heat to and remove heat from the working fluid, the

working fluid container preferably is in communication with means fortransmitting heat to and removing heat from the working fluid containedin the working fluid container. The same means may perform both heatingand cooling. Alternatively, the present invention could include separatemeans for performing each function.

According to one embodiment, the means for transmitting heat to andremoving heat from the working fluid is a heat exchanger. Dependingupon whether it is desired that the working fluid be heated or cooled,relatively warmer or relatively cooler water or other material may beintroduced into the heat exchanger. Preferably, a thermal hydraulic engine

according to the present invention includes one heat exchanger for eachworking fluid container, although an engine according to the presentinvention could include any number of heat exchangers.

FIG. 11 shows an embodiment of heat exchanger or working fluidcontainer according to the present invention. According to thisembodiment, the working fluid container 176 is surrounded by the heatexchanger 178.

This heat exchanger includes two openings, an inlet and an outlet. Arelatively hotter or cooler material may be introduced into the heat

exchanger to heat or cool the working fluid. Whether the working fluid isheated or cooled depends at least in part upon whether the material in theheat exchanger is relatively hotter or cooler than the working fluid. Theworking fluid container may include a plurality of fins or other devices toincrease the surface area of the working fluid container in contact with thematerial introduced into the heat exchanger.

Among other alternatives for increasing heat transfer to the working fluidis including a circulation pump in the working fluid container. Acirculation pump can create turbulent flow for increased heat transferspeed.

The heat exchanger is one example of a means for transmitting heat to orremoving heat from the working fluid. The heat exchanger can be builtaround the working fluid container whether part of a containment systemor not. In a heat exchanger, typically, high and low temperature fluids arebrought into contact with the working fluid container. Typically, the fluidcirculating through the heat exchanger is under relatively low pressure.However, the working fluid changes temperature, depending upon whether


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it is desired to heat or cool the working fluid. Therefore, the heatexchanger preferably is also constructed of a material capable ofwithstanding the pressures and temperatures that the fluid circulatingthrough it is at. Examples of materials that may be utilized in the heatexchanger are polyvinylchloride (PVC) pipe, metal pipe such as carbon

steel, copper, or aluminum, cast or injected molded plastic, or acombination of any materials capable of withstanding the pressures andtemperatures involved in the heat exchanger.

It is not necessary that only a liquid be utilized in the heat exchanger totransmit heat to or remove heat from the working fluid. For example,gases or a combination of liquid and gases may also be used in the heatexchanger to heat and/or cool the working fluid.

One advantage of the present invention is that any high and lowtemperature source material, whether liquids, or gases or transmitted by

another means may be used to heat and cool the working fluid. Forexample, heated waste water from industrial processes could be used totransmit heat to the working fluid. Such water typically is cooled in somemanner before being discharged to the environment. Therefore, rather thanbeing wasted, the heat in this water could be utilized in the presentinvention to produce mechanical and/or electrical energy. As stated above,solar heating and cooling could also be used according to the presentinvention. It is this ability to utilize heat and cooling from unutilizedsources, such as waste heat, or free sources, such as the sun, that makesthe present invention so desirable.

If a fluid is used in the heat exchanger, preferably, the liquid and/or gasshould be under at least some amount of pressure to ensure that the liquidsand/or gases flow through the heat exchanger. As the heated liquid and/orgas moves through the heat exchanger, it will transfer its greater heatenergy to the working fluid having a lower heat energy. The working fluidwill then expand, applying force against a piston, flexible barrier or othermember, thereby producing mechanical energy.

When the working fluid has absorbed as much heat as is possible or as isdesired from the heat exchanger, a relatively cooler liquid and/or gas maybe transferred through the heat exchanger. The heat in the working fluidwill then, according to natural laws, flow to the relatively cooler liquidand/or gas in the heat exchanger.

FIG. 22 shows an alternative embodiment of a heat exchanger accordingto the present invention. According to this embodiment, the heatexchanger 212 is located within the working fluid container 214.According to this embodiment, the working fluid container is alsocontinuous with the piston. According to other embodiments that include


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the heat exchanger within the working fluid container, the working fluidcontainer may not be continuous with the cylinder. In FIG. 22, distance arepresents the travel of the piston between its maximum positions at thepower and return strokes. The end 216 of the working fluid container 214may be sealed with a flange 218 secured between a flange 220 on the

working fluid container and an end flange 22 secured to the working fluidcontainer flange 220 with bolts 224.

FIG. 5 shows a simple version of a three cylinder engine according to thepresent invention. The components shown in FIG. 5 may not necessarilybe in the same physical position in relation to each other in the engine andare shown here in this arrangement for ease of understanding. The enginemay also include other components not necessary include in theseembodiments or shown in this Figure.

The engine shown in FIG. 5 includes three cylinders 100, 102 and 104. A

piston 106, 108, and 110, respectively, is disposed within each of thecylinders. Each of the pistons is connected to a connecting rod, 112, 114,and 116, respectively, that is connected to a crank shaft 118.

The number of cylinders and pistons included in the invention may vary,depending upon the embodiment and factors described above. An engineutilizing a piston such as that shown in FIGS. 14 and 15 may utilize onlytwo cylinders and pistons since the pistons will be pushed back into thecylinder by the working fluid entering the side of the cylinder where thepiston is attached to the connecting rod. This is because there is less of aneed to maintain the speed of the engine to ensure that the pistons will

travel back into the cylinders than is necessary when a power a returnstroke is not utilized. Accordingly, without utilizing the power returnstroke and only utilizing forward power stroke, it is preferable that theengine include at least three cylinders.

Due to the slow moving nature of the pistons in an engine according to thepresent invention, it may be necessary to include three pistons to ensurethat the pistons will complete their return stroke. With three pistons, atleast one piston will always be in a power stroke, to help ensure that otherpiston will help complete their return stroke. This occurs because the onepiston is always in the power stroke will be furthering the rotation of thecrank shaft thereby helping to move the other pistons along their returnstroke.

However, an engine according to the present invention may include anynumber of cylinders. For instance, engines can be built with 16, 20, ormore cylinders for larger electric power plant operations.


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The crank shaft is interconnected with a load. The load could be amechanical device driven by the crank shaft. Another example of a loadcould be an electric generator that is driven by the crank shaft. The crankshaft is also connected to a water valve 122 that controls the flow of highand low temperature liquid and/or gas into the heat exchangers.

The cylinders 100, 102, and 104 are each interconnected via a highpressure hose, 124, 126, and 128, respectively, to a working fluidcontainer, 130, 132, and 134, respectively. The working fluid containers130, 132, and 134 are enclosed within heat exchangers 136, 138, and 140,respectively. The working fluid may be contained within the space definedby the heat exchangers 130, 132, and 134, the high pressure connectors124, 126, and 128 and the interior of the cylinders 100, 102, and 104. Ofcourse, in embodiments that include a fluid containment system, theworking fluid is contained within the working fluid container. As isevident, in embodiments without the working fluid containment system,

the space that the working fluid is contained in changes volume as thepiston moves within the cylinder.

FIG. 6 shows a series of depictions of the three cylinder engine shown inFIG. 5 as the cylinders cycle. In the embodiment shown in FIG. 6, 141represents an off-center lo