Steam Engine Device and Methods of Use

FIELD OF THE INVENTION

The present invention relates to engines and more particularly to steam engines.

BACKGROUND

The use of pressurized steam may be an effective means of generating motive energy in an engine. A conventional steam engine may include, for example, a boiler, partially filled with water, which is heated by a fire such that the water is converted to steam. The steam may be pressurized and routed through pipes into, for example, a cylinder where it may force a piston to move.

Such a steam engine may be used to provide power, for example, for locomotives and ships. On a locomotive, the piston may be attached to one or more wheels by a drive rod and a coupling rod. A boiler may generate steam that is pressurized and routed to move a piston. As the piston moves, it forces the drive rod and the coupling rod to move back and forth, providing force to turn the wheels of the locomotive. On a ship, the piston may be connected to a crankshaft that causes a propeller to turn.

Conventional steam engines may have disadvantages in their structure and operation. The boiler of a conventional steam engine may contain high pressure steam during operation. If the boiler ruptures, it may cause a catastrophic explosion. Boilers and the water within may require a substantial amount of time to heat and to generate enough steam to begin generating power. Additionally, when a conventional steam engine is turned off, a substantial amount of energy may be wasted as the unused steam condenses and the water in the boiler cools.

SUMMARY

Embodiments of the present invention may provide steam engine devices and methods of use. One embodiment of the present invention provides a steam engine comprising a water pump system, and a steam generation system comprising an electric heating element configured to convert water received from the water pump system into pressurized steam as the water is pumped into the steam generation system. The steam engine may further comprise a power generation system configured to receive the pressurized steam from the steam generation system and generate energy.

This illustrative embodiment is provided as an example to aid in understanding of the present invention. As will be apparent to those of skill in the art, many different embodiments of steam engines and methods of use according to the present invention are possible. Additional uses, advantages, and features of the invention are set forth in the illustrative embodiments discussed in the detailed description herein and will become more apparent to those skilled in the art upon examination of the following.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other features, aspects and advantages of the present invention may be better understood when the following Detailed Description is read with reference to the accompanying drawings.

FIG. 1 is a diagrammatic view of components of a steam engine showing a power stroke in one embodiment of the present invention.

FIG. 2 is a diagrammatic view of components of the steam engine of FIG. 1 showing an exhaust stroke.

FIG. 3 is a diagrammatic view of a steam generation system in one embodiment of the present invention.

FIG. 4 is a diagrammatic view of components of the steam engine of FIG. 1 showing an exhaust stroke.

FIG. 5 is a diagrammatic view of components of the steam engine of FIG. 1 showing an exhaust stroke.

FIG. 6 is a diagrammatic view of components of a steam turbine engine in one embodiment of the present invention.

FIG. 7 is a flowchart showing a method of generating energy according to one embodiment of the present invention.

FIG. 8 is a diagrammatic view of an electric heater element in one embodiment of the present invention.

DETAILED DESCRIPTION

Embodiments of the present invention may provide a steam engine device and methods of using a steam engine.

An example of a steam engine according to one embodiment of the present invention comprises a water pump system, a steam generation system, and a power generation system. The power generation system may include a piston within a cylinder, in which the piston is connected to, for example, a crankshaft. The water pump system may pump water from a water supply into the steam generation system. The steam generation system may comprise an electric heating element, adapted to rapidly heat the water, converting it to steam. In one embodiment, the heating element comprises an electric tube heater. In one embodiment, the heating element comprises an electric probe heater. In one embodiment the heating element may be powered by a battery. For example, a suitable heating element may comprise a 1700 watt electric tube heater. Other suitable heating elements may comprise heating elements up to or greater than 5000 watts. Such heating elements may rapidly convert water to pressurized steam.

The pressurized steam may be pressurized and injected into the cylinder through a steam inlet when the piston is near a first end of the cylinder. The pressurized steam exerts a force on the piston, which causes it to move towards the second end of the cylinder. The forced motion of the piston towards the second end of the cylinder is referred to as the “power stroke” because the pressurized steam may be used to generate energy capable of powering a machine. When the piston is near the second end of the cylinder, the injector valve may be closed, which may reduce or cut off the supply of steam, and an exhaust valve at the first end of the cylinder opens. The rotational momentum of the crankshaft may push the cylinder back towards the first end of the cylinder, which may force steam out of the cylinder through the exhaust valve. The motion of the piston towards the first end of the cylinder is referred to as the “exhaust stroke” because this motion causes pressurized steam within the cylinder to be forced out of the cylinder through the exhaust valve. Once the piston is near the first end of the cylinder, the exhaust valve may close and the next power stroke may begin. An alternating series of power and exhaust strokes may be used to maintain motive energy to operate a machine, for example, to power rotation of a crankshaft. In an embodiment of the present invention, a part of the power generated by the engine may be used, by way of an alternator, to charge a battery that supplies electricity for electric heating element in the steam generation system.

Certain embodiments of the present invention may have many advantages over conventional steam engines. By eliminating a boiler, embodiments of the present invention may eliminate the safety risk of a boiler explosion. In embodiments of the present invention comprising an electric heating element, engine startup times may be greatly reduced as compared to engines having a boiler, because there is no need to boil a large quantity of water. In addition, because a large quantity of water is not heated to a boil, fuel consumption and energy loss due to cooling and reheating water may be reduced. A further advantage of the present invention is reduced emission of pollution. Embodiments of the present invention may be electrically powered and only release steam, i.e. heated water vapor, as exhaust, rather than the chemicals produced by internal combustion engines that use petroleum-based fuels. A still further advantage is that embodiments of the present invention may be made small enough to be used to power small machines, such as a lawn mower. Other embodiments of the present invention may have some or all of these advantages. Further embodiments may have none of the these or may have additional advantages.

In an illustrative embodiment of such a steam engine, water may be pumped from a water tank onto a heating element in a steam generation system. In certain embodiments, the water may be pumped at a pressure of at least approximately 1000 pounds per square inch (“PSI”). The heating element may be an electric heating element powered, for example, by a battery. The heating element may convert the water into high pressure steam and inject the steam into one end of a cylinder chamber comprising a piston that may travel the length of the cylinder. The steam may be injected into the cylinder at substantially the same time the piston is nearest a first end of the cylinder from which the steam is injected. The pressure generated by the steam forces the cylinder to travel away from the first end of the cylinder towards a second, opposite end of the cylinder. The piston may be connected to a crankshaft by a connecting rod such that when the piston reaches its closest position to the second end of the cylinder, the piston stops and is forced back towards the first end of the cylinder by the rotational inertia of the crankshaft, which in turn causes steam to be forced out of the cylinder through the exhaust valve. At substantially the point, or time, at which the piston stops traveling towards the second end of the cylinder, injection of steam into the cylinder may be stopped and an exhaust valve may be opened, which allows steam to escape from the cylinder. As pressurized steam is released from the cylinder through the exhaust valve, the piston moves back towards the first end of the cylinder. Movement of the piston toward the first end of the cylinder helps force steam out of the cylinder through the exhaust valve. When the piston nears the first end of the cylinder, the exhaust valve closes, and this cycle may be repeated, beginning with water being pumped at high pressure into the steam generation system.

In an illustrative embodiment shown in FIGS. 1 and 2, the steam engine 100 may comprise two systems: a fueling system 124 and a power generation system 125. The fueling system 124 may comprise components to pump water onto a heater element in a steam generation system 114. In the steam generation system 114, the water may be heated and converted to steam, which may be injected into the power generation system 125 at a pre-determined time. The power generation system 125 may comprise components for using pressurized steam from the fueling system 124 to generate energy capable of powering operation of a machine.

In the embodiments shown in FIGS. 1, 2 and 3, the steam generation system comprises a housing, a water injector line, an electric probe heater 114 having positive and negative electrical leads 305, 306, and a steam outlet 115. FIG. 3 shows a diagram of the steam generation system 114 of a steam engine in which an electric current is used to power the heating element. In the embodiment shown, the probe heating element 304 is capable of being heated to about 1000-1400 degrees Fahrenheit (F). Other embodiments may comprise heating elements capable of being heated to higher or lower temperatures. Embodiments may comprise heating elements configured other than as a probe heater, for example a coil heating element. The probe heating element 304 may be heated when electricity is passed from an electric power supply (not shown) through the probe heating element 304. Electricity may be supplied from the electric power supply, such as a battery, via the positive electric line 305. The electrical current flows through to the negative electrical line 306, which may be connected to the power supply.

In the embodiment shown in FIGS. 1-3, when the probe heating element 304 is operating within a temperature range of 1000-1400 degrees F., water may be injected at high pressure through the water injector line 302 such that it contacts the probe heating element 304 and is converted to pressurized steam. The steam in the steam generation system 114 may be pressurized to approximately 1000 PSI. The pressurized steam may pass out of the steam generation system 114 through the steam outlet 307. In such an embodiment, the steam outlet 307 may be configured to channel pressurized steam into the power generation system 125 of the steam engine 100. In another embodiment, the steam outlet 307 may channel steam into a pressure vessel (not shown) for later storage and injection into the power generation system 125 of the steam engine 100.

The fueling system 124 may comprise a water storage tank 101, a main water pipe 102, a pump 104, an injector valve 110, and steam generation system 114. The fueling system 124 may include other components such as a line strainer 103, an unloader valve 106, a bypass pipe 107, an accumulator 108, an injector cam 112, a pressure gauge 105 and a flow control valve 109. Embodiments of the present invention may use fluids other than water that may be pumped under pressure and heated to create a gas capable of moving a piston. Alternatively, an embodiment may utilize a power generation mechanism that pressurizes an existing gas for moving a piston.

Embodiments of the present invention may include various combinations of the fueling system 124 components described herein. Some embodiments may comprise additional fueling system 124 components. For example, an embodiment of the present invention may comprise a pressure release valve (not shown) to allow water or steam to flow out of the steam engine if the water or steam pressure becomes greater than a threshold.

The fueling system 124 components may be interconnected and operate in combination to provide fuel to the power generation system 125. For purposes herein, an “upstream” component is defined as a component located upstream relative to a particular component in the direction of the water tank 101. A “downstream” component is defined as a component located downstream relative to a particular component in the direction of the power generation system 125. For example, referring to FIG. 1, the line strainer 103 is located upstream from the pump 104, while the pressure gauge 105 is located downstream from the pump 104.

In the embodiment shown in FIGS. 1 and 2, the components of the fueling system 124 are interconnected. The main water pipe 102 provides a means for water to flow from the water tank 101 to the steam generation system 114, the water tank 101 being at the upstream end of the main water pipe 102, and the heater element 114 at the downstream end of the main water pipe 102. Between the water tank 101 and the heater element 114, the pump 104 is connected in-line to the main water pipe 102. Downstream of the pump 104, the injector valve 110 and injector valve cam 112 may be located in-line to the water pipe. The injector valve cam 112 may be configured to periodically open and close the injector valve 110. These components are connected such that when the pump 104 is activated, water may be pumped from the water tank 101 into the main water pipe 102, through the pump 104, and into the injector valve 110. The injector valve cam 112 actuates opening and closing of the injector valve to inject pressurized water into the steam generation system 114 in a manner relative to timing of movement of the piston 117 in the power generation system 125.

Embodiments of the present invention may comprise pumps of varying size and pressure ratings. For example, in the embodiment shown, the pump 104 may be capable of pumping and maintaining a constant supply of water to the injector valve at a pressure of at least 1,000 PSI. Other embodiments may comprise pumps capable of pumping water at pressures greater than or less than 1,000 PSI. Other embodiments may comprise multiple pumps.

Embodiments of the present invention may comprise one or more accumulators. The accumulator 108 may be used to eliminate or minimize changes in water pressure within the fueling system 124 as the injector valve 110 opens and closes. During operation of an embodiment of the present invention, the accumulator 108 may be partially filled with pressurized water. Just as the injector valve 110 opens, the fueling system 124 may experience a loss in water pressure as water exits the main water pipe 102 to enter the steam generation system 114. To maintain a constant water pressure, the accumulator 108 may re-introduce some or all of its water into the main water pipe 102. Further, just as the injector valve 110 is closed, the main water pipe 102 may experience an increase in water pressure as water is prevented from flowing into the steam generation system 114. The accumulator 108 may partially or completely fill with water to reduce the pressure within the main water pipe 102.

In one embodiment of the present invention, the water pump system may comprise a pressure gauge 105. The pressure gauge 105 may be used to monitor pressure within the water pump, or fueling, system 124. For example, a lower than expected pressure reading on the pressure gauge 105 may indicate a leak in the fueling system 124. A higher than expected reading may indicate that an adjustment is needed to a component within the fueling system 124, such as the unloader valve 106. Further, the pressure gauge 105 may indicate when pressure in the fueling system 124 is no longer within a safe pressure range. The pressure gauge 105 may have other functions, for example, in conjunction with other components to provide an engine that is capable of self-regulation of water pressure or shutting itself off if pressure levels indicate a malfunction.

As shown in the embodiments in FIGS. 1 and 2, the fueling system 124 may further include unloader valve 106 and bypass pipe 107. The unloader valve 106 may be connected to the main water pipe 102 downstream from the pump 104 and upstream from the injector valve 110. The unloader valve 106 may be further connected to the bypass pipe 107, which connects to the main water pipe 102 at a point upstream from the pump 104. When the unloader valve 106 is open, water may flow from the main water pipe 102 into the bypass pipe 107. Conversely, when the unloader valve 106 is closed, water is prevented from flowing from the main water pipe 102 into the bypass pipe 107. Between the connection point of the bypass pipe 107 to the main water pipe 102 and the pump 104, a line strainer 103 may be connected in-line to the main water pipe 102 to strain undesired impurities from the water. Downstream from the unloader valve 106, the accumulator 108 may be connected to the main water pipe 102 between the unloader valve 106 and the injector valve 110. The flow control valve 109 may be connected to the main water pipe 102 between the accumulator 108 and the injector valve 110. The pressure gauge 105 may be connected between the pump 104 and the unloader valve 106.

In the embodiments shown in FIGS. 1 and 2, the various components of the water pump system 124 operate to provide water to the steam generation system 114, which in turn heats and converts the water into steam for injection into the power generation system 125 of the steam engine 100.

As the embodiments of the steam engine 100 shown in FIGS. 1 and 2 operate, the injector valve cam 112 controlling the injector valve 110 rotates and periodically opens and closes the injector valve 110. The cam 112 may have a small protrusion that, as the cam 112 rotates, contacts the injector valve 110 and displaces the injector valve 110, causing it to open. As the protrusion rotates out of contact with the valve 110, the valve 110 is no longer displaced and it closes. This periodic opening and closing of the injector valve 110 creates a cyclic introduction of pressurized water into the steam generation system 114, where steam is generated for injecting into the power generation system 125 of the steam engine 100. Other embodiments of the present invention may use another method to open the injector valve 110. For example, the cam 112 may cause a periodic opening and closing in a manner other than by rotation. In still other embodiments, the injector valve 110 may be periodically opened and closed by hydraulic lifters instead of the cam 112. For example, a fluid may be periodically allowed to flow into the lifter, which then actuates the lifter with hydraulic pressure, causing the injector valve 110 to open. When the hydraulic pressure is released, the lifter returns to a rest position and the valve 110 closes.

For illustrative purposes, fueling system 124 operation is described in the context of a single cycle of the opening and closing of the injector valve 110, comprising the following events: steady-state while the injector valve 110 is closed during the exhaust stroke; the transition state when the injector valve 110 is opening; steady state while the injector valve 110 is open during the power stroke; the transition state while the injector valve 110 is closing; and the steady state while the injector valve 110 is closed during the exhaust stroke.

During the steady state period when the injector valve 110 is closed, the pump 104 remains active and continues to pump water through the main water pipe 102. In an alternative embodiment, the pump 104 may deactivate upon closing of the injector valve 110. While the injector valve 110 is closed, pressure may build up within the main water pipe 102. If pressure exceeds a pre-determined level, the unloader valve 106 may open so that water flows through the bypass pipe 107 back into the main water pipe 102 upstream from the pump 104. This creates a closed loop through which water may flow while the injector valve 110 is closed in order to maintain a pressure within a desired range in the fueling system 124. In addition to flowing through the bypass pipe 107, water may flow into the accumulator 108, where it may be stored for use on demand. Because the injector valve 110 is closed during this steady state period, no water flows into the steam generation system 114, and hence no steam is produced in this phase.

After a predetermined period of time, the injector valve 110 may be opened by the injector valve cam 112, allowing water to begin to flow through the injector valve 110. During this phase, as water begins to flow through the injector valve 110, the pressure in the main water pipe 102 begins to drop. At this point, the unloader valve 106 may close to prevent water from flowing through the bypass pipe 107. In one embodiment, the unloader valve 106 may be responsive to pressure. In one embodiment, the unloader valve 106 may be responsive to the flow of fluid. To minimize the pressure fluctuation in the main water pipe 102, the accumulator 108 may reintroduce a portion, or all, of its accumulated supply of water into the main water pipe 102, helping to maintain a relatively constant water pressure in the main water pipe 102. The flow control valve 109 may be used to regulate the volume of water that passes out of the main water pipe 102 for conversion to steam, thereby providing a throttling effect. Some embodiments of the present invention may be adapted to operate without a flow control valve. For example, in one embodiment of the present invention, the injector valve may be configured such that it may be opened to allow varying amounts of water to pass through the valve. In such an embodiment, regulation of the volume of water that passes out of the main water pipe 103 for conversion to steam may be accomplished by adjusting the amount of water the injector valve allows to pass through it.

When the unloader valve 106 is closed to the bypass pipe 107, water continues to flow past the unloader valve 106 and the bypass pipe 107, through the injector valve 110, and into the steam generation system 114 where it is converted to steam to be provided to the power generation system 125. When the injector valve 110 closes, the unloader valve 106 reopens to allow water to flow into the bypass pipe 107. Water may also flow into the accumulator 108. This priming cycle in the fueling system may repeat in coordination with the operation of the power generation system while the steam engine 100 is in operation.

The power generation system 125 comprises components for generating energy from pressurized steam provided by the water pump system 124 as it is needed by the power generation system 125. As shown in the embodiments in FIGS. 1 and 2, the power generation system 125 may comprise a piston 117 within a cylinder 123 such that the piston 117 may slide “up” and “down” within the cylinder 123. For the purposes herein, “up” is defined as piston motion toward the first end of the cylinder 123 away from the crankshaft 121 in direction 119, and “down” is defined as piston motion toward the second end of the cylinder 123 and the crankshaft 121 in direction 118. “Up” and “down” are not intended to limit the orientation of a cylinder in embodiments of the present invention, but merely to provide convenient terminology for describing the motion of the piston. In embodiments of the present invention, the cylinder may be oriented in any direction.

As shown in the embodiments in FIGS. 1 and 2, the first end of the cylinder 123 may be sealed by a cover. The cover may have two openings, one of which may be controlled by an exhaust valve 116, the other opening may be a steam inlet 115. In an embodiment, the exhaust valve 116 may be opened and closed by an exhaust cam 113. In another embodiment, the exhaust valve 116 may be opened and closed by hydraulic lifters. The piston 117 may be connected to a crankshaft 121 such that when the piston 117 moves up and down within the cylinder 123, the sliding motion of the piston 117 will cause the crankshaft 121 to rotate 122.

The power generation system 125 may operate in a single power cycle, meaning that the piston 117 is driven by pressurized steam on every downstroke 118. In the embodiments shown in FIGS. 1 and 2, the full power cycle is shown in two phases: the power stroke in FIG. 1 and the exhaust stroke in FIG. 2. At the beginning of the power stroke, the piston 117 is near the first end of the cylinder 123 and steam from the steam generation system of the fueling system 124 is injected into the cylinder 123. Pressurized steam may continue to be injected into the cylinder for most or all of the duration of the power stroke 123. The pressure of the steam forces the piston 117 towards the second end of the cylinder 123, causing the crankshaft 121 to rotate 122. When the piston 117 has reached the point of its motion nearest the second end of the cylinder 123, the power stroke ends and the exhaust stroke begins. Near the end of the power stroke and the beginning of the exhaust stroke, the movement of the injector valve cam 112 closes the injector valve 110, thereby stopping the injection of steam into the cylinder 123. Simultaneously, or nearly simultaneously, with the closing of the injector valve 110, the exhaust valve 116 opens. The piston 117 is forced back towards the first end of the cylinder 123 by the rotational momentum of the crankshaft 121, and steam vents through the exhaust valve 116. When the piston 117 has reached the point of its motion nearest the first end of the cylinder 123, the exhaust stroke ends and the next power stroke begins. The exhaust valve 116 closes and pressurized steam may again be injected into the cylinder 123 from the fueling system 124 to begin the next power stroke.

In an aspect of the present invention, the steam generation system 114 of the fueling system 124 may be powered with an electrical current. For example, in an embodiment the electrical current may be provided by a battery (not shown). In such an embodiment, the battery may provide electrical power to operate the steam generation system 114 and an electric motor within the pump 104. In an embodiment of the present invention, an alternator (not shown) may be advantageously coupled to the crankshaft 121 such that a portion of the energy generated by the rotation of the crankshaft 121 may be used to recharge the battery. Such a configuration may be advantageous because it may increase the efficiency of the engine 100, by reducing the drain of power from the battery.

A further advantage of some embodiments of the present invention may be that, rather than requiring a large boiler tank as with conventional steam engines, the fueling system 124 of the present invention may utilize a small, electrically powered steam generation system 114 to provide steam to the power generation system 125. An embodiment of the present invention thus may provide safety advantages by eliminating the need for the maintenance of a large vessel containing high pressure, high temperature gas. A further advantage is that an embodiment of a steam engine according to the present invention may be more efficient because it may use less energy to generate steam than conventional steam engines. In addition, an embodiment of the present invention may be more efficient because the time required to begin generating energy in embodiments of the present invention may be less than for a steam engine comprising a boiler. Another advantage may be that the water pump system 104 and steam generation system 114 may be powered, at least in part, by the energy generated by the steam engine 100.

Embodiments of the present invention may be advantageously utilized in a variety of applications. For example, an embodiment of a steam engine of the present invention may be utilized to power a machine, such as a lawn mower or leaf blower. An embodiment may be used as an electric generator to generate electrical power. An embodiment of the present invention may be adapted to power vehicles, such as automobiles, boats, motorcycles, trucks, buses or locomotives. Additional uses of embodiments of the present invention would be apparent to one of skill in the art.

FIGS. 4 and 5 show a diagrammatic view of a steam engine in another embodiment of the present invention. The embodiment shown comprises a water pump system (not shown) and a steam generation system comprising an electric heater element 114 configured to convert water received from the water pump system into pressurized steam substantially as the water is pumped into the steam generation system. The steam generation system in the embodiment shown in FIGS. 4 and 5 comprises an injector valve and a camshaft coupled to a cam configured to open and close the injector valve. The steam generation system is configured to receive water through a water inlet, channel water to the electric heating element, and expel pressurized steam through a steam outlet 115. The steam engine shown in FIGS. 4 and 5 further comprises a power generation system configured to receive the pressurized steam from the steam generation system and generate energy.

In such an embodiment, the steam engine may comprise a cylinder as may be configured in an internal combustion engine that has been modified to operate using pressurized steam rather than a combustible fuel/air mixture. The embodiment shown in FIGS. 4 and 5 comprises a piston 401 disposed within a cylinder 402 comprising a first end 412 and a second end 413. The piston 401 is configured to slide back and forth between the first end and the second end of the cylinder 402. The piston 401 is coupled to a crankshaft 408 by a connecting rod 409. Two exhaust valves 403, 404 near the first end 412 of the cylinder 402 are configured to be periodically contacted by camshaft lobes 406, 407 coupled to a camshaft 405. In a conventional internal combustion engine, one of valves 403 or 404 may be a fuel intake valve and the other may be an exhaust valve. However, because pressurized steam is injected into the cylinder from steam inlet 115, a valve for allowing fuel intake is not necessary and both valves may be used as exhaust valves.

The camshaft lobes 406, 407 may be oriented such that the lobes 406, 407 are approximately 180 degrees out of phase relative to each other. The camshaft may be coupled to camshaft gear 411, which is coupled to a crankshaft gear 410. As in the embodiment shown, the gear ratio of the camshaft gear 411 and crankshaft gear 410 may be 2 to 1, where the camshaft gear 411 is the larger of the two gears. Heater element 114 may be coupled to the first end of the cylinder 402 and may be configured to provide steam to the cylinder 402 through steam inlet 115.

The embodiment shown in FIGS. 4 and 5 may operate as a two-cycle engine. A two-cycle engine is an engine in which every down stroke of a piston is a power stroke. In contrast, in a four-cycle engine, every other down stroke of a piston is a power stroke. During operation, the piston 401, in the embodiment shown, slides up and down, or back and forth, within the cylinder 402. When the piston 401 is near the first end 412 of the cylinder 402, pressurized steam may be injected into the cylinder 402 through steam inlet 115, causing the piston 401 to move towards the second end 413 of the cylinder 402. When the piston 401 is near the second end 413 of the cylinder 402, pressurized steam is no longer injected into the cylinder 402 and camshaft lobe 406 contacts the exhaust valve 404, causing it to open, while the exhaust valve 403 remains closed as shown in FIG. 4. The piston 401 is then moved towards the first end 412 of the cylinder 402 by rotational momentum of the crankshaft 408. As the piston 401 moves towards the first end 412 of the cylinder 402, steam within the cylinder 402 is forced out of the cylinder 402 through the open exhaust valve 404. When the piston 401 is near the first end 412 of the cylinder 402, the camshaft lobe 406 moves out of contact with the exhaust valve 404, allowing it to close. Steam may then be injected into the cylinder 402, beginning the next cycle. The next cycle proceeds like the previous cycle, however, during this cycle, camshaft lobe 407 contacts exhaust valve 403, causing it to open, while exhaust valve 404 remains closed, as shown in FIG. 5. These cycles may be repeated to maintain rotation of the crankshaft 408.

As described above, the exhaust valves 403, 404 may be opened as camshaft lobes 406, 407 contact the exhaust valves. The camshaft lobes 406, 407 may be coupled to the camshaft 405 such that the camshaft lobes 406, 407 rotate with the camshaft 405. As a camshaft lobe rotates, it may contact its corresponding exhaust valve, thereby opening the valve. The camshaft 405 may be coupled to the camshaft gear 411, and rotate with the camshaft gear 411. The camshaft gear 411 may be rotated by the crankshaft gear 410, which may be coupled to the crankshaft 408. The ratio of the crankshaft gear 410 to the camshaft gear 411 determines, at least in part, the rate at which the camshaft lobes 406, 407 open the exhaust valves 403, 404. In the embodiment shown, the camshaft gear 411 has approximately twice the number of teeth as the crankshaft gear 410. Thus, for approximately every two rotations of the crankshaft gear 410, the camshaft gear 411 will rotate approximately once. This ratio means that each exhaust valve will open once for every two crankshaft 408 rotations, or one of the exhaust valves will open for each rotation of the crankshaft gear 410.

Other embodiments may have different ratios between the crankshaft gear 410 and the camshaft gear 411. However, the number and placement of the camshaft lobes may be affected by the gear ratio. For example, in an embodiment where the ratio between the crankshaft gear 410 and the camshaft gear 411 is 1 to 1, the camshaft gear 411 will rotate once for every rotation of the crankshaft gear 410. In such an embodiment, the camshaft lobes 406, 407 may be in phase with each other, such that both lobes contact their respective exhaust valves at approximately the same time. In such an embodiment, each exhaust valve would open for every rotation of the crankshaft 408. Various embodiments may have different gear ratios and use different numbers of valves.

The embodiment shown in FIGS. 4 and 5 comprises two exhaust valves. Other embodiments may comprise one or three or more valves. Further, while the two valves 403, 404 in the embodiment shown in FIGS. 4 and 5 are configured to open on alternating exhaust strokes, other embodiments may have different camshaft lobe orientations and/or different camshaft gear 411 to crankshaft gear 410 ratios, that may allow both valves to open simultaneously or with different frequencies.

Some embodiments of the present invention may comprise a plurality of the cylinder configurations shown in FIGS. 4 and 5. For example, an embodiment of the present invention may comprise two cylinders. The cylinders may be coupled to the same crankshaft, or each cylinder may be coupled to its own crankshaft. In an embodiment, two cylinders, as described with respect to FIGS. 4 and 5, are coupled to the same crankshaft. The two cylinders may be configured to receive pressurized steam at substantially the same time, such that each cylinder is in its power stroke at substantially the same time as the other cylinder. In another embodiment, the cylinders may be configured such that as one cylinder is performing its power stroke, the other cylinder is at a different position within its power stroke, or is within its exhaust stroke.

Other embodiments of the present invention may comprise more than two cylinders. For example, an embodiment of the present invention may comprise six cylinders. In such an embodiment, each cylinder may be coupled to the same crankshaft. The cylinders may also be configured such that the six cylinders operate as three pairs of substantially synchronized cylinders. In such an embodiment, for example, a first cylinder and a second cylinder may operate such that they perform a power stroke at substantially the same time, and perform an exhaust stroke at substantially the same time. In such an embodiment, a third cylinder and a fourth cylinder may comprise a second pair of substantially synchronized cylinders, and a fifth cylinder and a sixth cylinder may comprise a third pair of substantially synchronized cylinders. In such an embodiment, each cylinder within a pair of cylinders may be synchronized with the other cylinder within the pair, but each pair of cylinders may not be synchronized with any other pair of cylinders. Other embodiments may further comprise more than two cylinders and may or may not comprise pairs or other groupings of synchronized cylinders.

FIG. 6 shows a diagrammatic view of a steam turbine engine in an embodiment of the present invention. This embodiment comprises a fueling system 610 and a power generation system 611. The fueling system 610 comprises components as described above with reference to FIGS. 1 and 2 above. Such a water pump system may include an injector valve or an injector valve cam. The fueling system 610 shown in FIG. 6 is configured to continually inject water into the heater element 114 as long as the pump 104 is operating and flow control valve 109 is open. For example, the fueling system 610 may include a water pump system. Accordingly the water pump system 610 may operate without an injector valve or an injector valve cam. The flow of water into the heater element 114 may be controlled by flow control valve 109. Flow control valve 109 may be controlled manually or automatically. For example, flow control valve 109 may be controlled by a computer, which is configured to automatically adjust the flow control valve 109.

In the embodiment shown in FIG. 6, the power generation system 611 may comprise a turbine 601, an exhaust port 603 and an output shaft 602. The turbine 601 may comprise a plurality of turbine blades and is coupled to the output shaft 602 such that as the turbine 601 rotates, it causes the output shaft 602 to rotate. In some embodiments, the turbine 601 may be directly coupled to the output shaft 602, such that output shaft 602 rotates approximately 360 degrees for every approximately 360 degrees of turbine 601 rotation. In other embodiments, the turbine 601 may be indirectly coupled to the output shaft 602, such that the output shaft 602 rotates approximately 360 degrees or more or less than 360 degrees for every approximately 360 degrees of turbine 601 rotation. The turbine 601 blades may be configured such that as pressurized steam entering the turbine 601 from the steam inlet 115 contacts the turbine blades, the turbine blades may be displaced and thereby cause the turbine 601, and consequently, the turbine shaft 602, to rotate.

During operation, pressurized steam may be forced into the turbine through steam inlet 115. The pressurized steam may force the blades of the turbine to move, thereby causing the turbine to rotate. Pressurized steam that has traveled past the turbine blades may be allowed to escape the turbine through the exhaust vent 603. By continually applying pressurized steam to the turbine blades, the rotation of the turbine may be maintained. In the embodiment shown, heater element 114 may be coupled to a battery (not shown), which may provide electric power to cause heater element 114 to heat to a sufficient temperature to convert water to high pressure steam. Additionally, flow control 109 may be adjusted to provide increased or decreased flow of water into heater element 114, which may cause increased or decreased amounts of pressurized steam to be expelled into turbine 601, which may cause turbine 601 to rotate at increased or decreased speeds.

In some embodiments of the present invention, a steam turbine engine may comprise a manifold (not shown) and a plurality of heater elements 114. For example, in one such embodiment, the plurality of heater elements may be configured to inject steam into a turbine 601. Water may be pumped from a single water pipe into the manifold, which may then distribute the water to the plurality of heater elements, creating pressurized steam, which may then be injected into a second manifold, which combines the flow of pressurized steam from the plurality of heater elements. The combined flow of pressurized steam may then be injected onto the turbine 601. Such an embodiment may be advantageous as a plurality of smaller, less expensive heater elements may be used, rather than a single, more expensive element. Such an embodiment may be advantageous as it may be capable of more efficiently turning a quantity of water into pressurized steam.

In one embodiment of the present invention, a steam engine may comprise a turbine 601 configured to generate electrical energy. For example, the steam turbine 601 may be coupled to an electric motor, such that the steam turbine 601 provides at least part of the electrical energy needed to power the electric motor. Such an embodiment may be advantageously employed to provide propulsion to a vehicle, such as an automobile or ship. A steam turbine 601 according to one embodiment of the present invention may be configured to transmit a portion of the generated electrical energy to a battery, such as a battery supplying electrical power to heater element 114. In one embodiment, the steam turbine 601 may supply electrical power to one or more batteries for storing energy for use in an electrically-powered car.

Embodiments of the present invention include certain methods, including methods of using or operating a steam engine. For example, an illustrative embodiment of the present invention may comprise providing water in a water tank, periodically pumping the water under pressure from the tank into a steam generation system, injecting steam from the steam generation system into a cylinder, driving a piston with pressurized steam to operate a machine, and exhausting steam from the cylinder. An embodiment of the present invention may further comprise the steps of providing a steam generation system comprising an electric heating element, providing electrical power to the electric heating element to heat the heating element, rapidly converting water to steam with the heating element, and delivering steam from the electric heating element out of the steam generation system to the power generation system.

FIG. 7 is a flowchart 700 showing a method of generating energy according to one embodiment of the present invention. The method shown in FIG. 7 begins with pumping water into a steam generation system, as shown in step 701. For example, a water pump may be employed to pump water from a water tank into a steam generation system as previously described. Water pumped into the steam generation systems is then rapidly converted into pressurized steam with an electric heating element in step 702. In the embodiment shown in FIG. 7, the water is rapidly converted to pressurized steam as the water is pumped into the steam generation system. For example, the water may be sprayed onto an electric heating element. In step 703, the pressurized steam is expelled from the steam generation system into the power generation system. The pressurized steam is converted to energy in step 704. For example, the pressurized steam may cause a turbine to spine.

In one embodiment of the present invention, a method for generating energy comprises pumping water through a water inlet valve into a steam generation system and about an electric heating element disposed within the steam generation system. For example, a steam generation system may comprise a tube heater. In such an embodiment, a tube heater may be disposed within the steam generation unit and may conform to the shape of a portion of the steam generation unit. For example, steam generation unit may comprise a water inlet configured to allow water to flow into the steam generation unit at an angle of approximately 90 degrees relative to the angle at which pressurized steam is expelled from the steam generation unit. In such an embodiment, a tube heater may be employed and configured (such as by bending) to accommodate part or all of the angle. In other embodiments, the angle at which water enters the steam generation unit may be related to the angle or plane at which pressurized steam exits the steam generation unit and the relation may be any angle greater than or equal to 0 degrees. In one embodiment, tube heater may comprise a coiled shape. Such ane embodiment may be advantageous because a straight tube heater may be replaced with a coiled tube heater, which may provide a more space-efficient tube-heater.

For example, FIG. 8 shows an electric heating element according to one embodiment of the present invention. FIG. 8 comprises an electric tube heater 800 having a tubular housing 801 that contains a heating element 804. Heating element 804 may be disposed within the housing such that a small space is defined between the housing 801 and the heater element 804 to allow steam to move through the electric tube heater 800 to the steam outlet. For example, in the embodiment shown in FIG. 8, the space between the heater element 804 and the housing 801 is approximately 1/16 of an inch. In other embodiments, the space may be greater than or less than 1/16 of an inch. The electric tube heater 800 shown in FIG. 8 further comprises a water injector line 802 through which water may be received from a water pumping system. In the embodiment shown, the water injector line has a diameter of approximately 1/16 of an inch. In other embodiments, the space may be greater than or less than 1/16 of an inch. In one embodiment, water may be continuously injected into the electric tube heater 800. In one embodiment, water may be periodically injected into the electric tube heater 800, such as, for example, through an injector valve that is opened and closed by a cam coupled to a camshaft. The electric tube heater 800 also comprises a steam outlet 803 through which pressurized steam may be expelled. In the embodiment shown in FIG. 8, the steam outlet 803 has a diameter of approximately ½ of an inch. In other embodiments, the steam outlet 803 may have a diameter of greater than or less than ½ of an inch. The electric tube heater may be powered by electricity transmitted through electrical leads 805 and 806. A portion of the electric tube heater 800 may comprise a ceramic insulator 807, or other insulation.

In the embodiment of the electric heating element shown in FIG. 8, electric tube heater 800 may be powered and generate heat. For example, in one embodiment electric tube heater 800 may be powered by with between approximately 12 240 volts. Other embodiments may comprise electric tube heaters powered by other voltages greater than 240 volts or less than 12 volts. In one embodiment, electric tube heater 800 may be powered by alternating current. In one embodiment, electric tube heater may be powered by direct current. In the embodiment shown, the electric tube heater may consume between approximately 250 and 2250 watts of power, though in some embodiments, electric tube heaters may consume greater than 2250 watts or power, or less than 250 watts of power. In the embodiment shown, the heating element 804 may be heated to approximately 1700 degrees Fahrenheit (1700 F.). Other embodiments may comprise electric tube heaters capable of being heated to temperatures greater than or less than 1700 F.

In the embodiment shown in FIG. 8, water may be injected into the electric tube heater 800, which has been heated to 1700 F. In one embodiment of the present invention, the water is not pre-heated prior to being injected into the electric tube heater 800. In one embodiment of the present invention, the water may be pre-heated to a temperature less than 212 F. (or 100 C.) in a water injector line, or in a water tank. As the water enters the tube heater, the water may be substantially immediately, or instantly, converted to steam. The water may travel a short distance within the electric tube heater 800 after injection, however, the water may be substantially immediately converted to steam as it encounters the heating element 804. In the embodiment shown, The steam may travel from the water inlet 802 to the steam outlet 803 because of pressure caused by the vaporization of the water. Further, as the steam moves through the electric tube heater 800, the steam may be additionally heated, which may cause an increase in the pressure of the steam. The pressurized steam may then be expelled from the electric tube heater 800 through steam outlet 803 into a power generation system, such as a piston engine or turbine, as described in other parts of this specification.

In one embodiment, pumping water may comprise maintaining a substantially constant pressure of water in a pumping system, opening an injector valve with a camshaft coupled to a cam to allow water to flow through the water inlet, and closing the injector valve to stop water from flowing through the water inlet. In one embodiment, pumping water may comprise maintaining a substantially constant pressure of water in a pumping system; and continuously injecting water into the steam generation system. Such embodiments may advantageously supply water at a substantially constant or uniform pressure to the steam generation system.

After pumping the water into the steam generation system and about the electric heating element, one embodiment of the present invention may comprise converting the water into pressurized steam in the steam generation system by heating the water with the electric heating element substantially immediately after pumping the water about the electric heating element. For example, water may be pumped into the steam generation unit and about the electric heating element, which may vaporize the water substantially immediately after the water contacts the electric heating element. Such an embodiment may be advantageous as high steam pressures may be generated very rapidly.

After converting the water into pressurized steam, one embodiment of the present invention comprises expelling the pressurized steam from the steam generation system into a power generation system. For example, in one embodiment, the steam generation system may comprise a cavity in which an electric heating element may be disposed. For example, the electric heating element may be disposed within the cavity and may allow for water to be pumped into the steam generation unit and about the electric heating element, and for pressurized steam to move past the electric heating element and out of the steam generation system through a steam outlet.

After expelling the pressurized steam from the steam generation system into a power generation system, one embodiment of the present invention may comprise converting the pressurized steam in the power generation system into motive energy. For example, the power generation system may comprise a piston coupled to a crankshaft. The pressurized steam may cause the piston to move, which may turn the crankshaft to generate mechanical energy or electrical. In one embodiment, the power generation system may comprise a turbine. In such an embodiment, the pressurized steam may cause the turbine to spin which may generate mechanical or electrical energy.

Some methods of generating energy according to embodiments of the present invention may comprise various combinations of the following steps: providing water in water tank; pumping water from the water tank; cycling water through the fueling system through an unloader valve and bypass pipe while an injector valve is closed; maintaining a substantially constant water pressure in the fueling system by using an accumulator; periodically opening the injector valve with an injector valve and injector valve cam; providing a steam generation system comprising an electric heating element; pumping water from the water tank; periodically opening and closing the injector valve to allow water to be pumped into the steam generation system; rapidly converting the water to steam; providing a cylinder having a first and second end; providing a piston disposed within the cylinder and configured to slide between the first and second ends of the cylinder and to cause a crankshaft to rotate; periodically injecting steam into the first end of cylinder when the piston is near the first end of the cylinder; and opening an exhaust valve when the piston is near the second end of the cylinder.

An embodiment of such a method may further comprise providing an alternator coupled to the crankshaft, generating electricity by rotating the crankshaft, providing generated electricity to the alternator, and charging the battery using the electricity supplied to the alternator.

Embodiments of the present invention include methods of operating a steam turbine engine, such as the embodiment described with respect to FIG. 6. For example, one embodiment of the present invention may be a method for using a steam turbine engine to generate electricity to power an electric vehicle, such as an electric car. Such an embodiment may comprise a battery, an alternator, and a steam turbine engine. The method of operation may comprise starting the steam engine using electrical power from the battery, operating the steam turbine to generate electricity, using the generated electricity to operate the car, and using the alternator to recharge the battery.

Embodiments of the present invention include methods of operating a steam engine, such as the embodiment described with respect to FIGS. 4 and 5. For example, one embodiment of the present invention may be used to power a machine. Another embodiment of the present invention may be used to generate electrical power. For example, an embodiment of the present invention may comprise the steps of powering a lawn mower by using a battery to start the steam engine, coupling the steam engine to a lawn mower blade, operating the steam engine at one or more speeds, using an alternator to recharge the battery, and using the lawn mower to cut grass.

The foregoing description of the embodiments of the invention has been presented only for the purpose of illustration and description and is not intended to be exhaustive or to limit the invention to the precise forms disclosed. Numerous modifications and adaptations thereof will be apparent to those skilled in the art without departing from the spirit and scope of the invention.

Steam Engine Device and Methods of Use

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CPC

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