Patent Application
20140178237
1. Field of the Invention
The present invention relates to a heat engine, and in particular in one embodiment to a rotary style heat engine and in another embodiment to a linear drive heat engine that can have any number of independent cylinders and one way clutches.
2. Description of the Related Art
Heat energy, sometimes called thermal energy, is defines as the kinetic energy of a system's particles. Put another way, the heat energy of a system is the amount of potential energy in a system that is derived from the heat content within the system.
Temperature is not the same as heat energy. Yet, temperature makes up an integral part of the ideal gas law. The ideal gas law states:
PV=nRT
Wherein:
P is Pressure
V is Volume
n is the amount of gas
R is the universal gas constant and
T is temperature
This ideal gas law demonstrates that temperature and pressure are directly related when the other variables are held constant. Likewise, when temperature is held constant in a closed system, the pressure and volume are inversely related.
This is demonstrated as follows:
P1*V1=P2*V2
That is, the sum of pressure times volume stays constant in a closed system when the temperature remains constant.
It is known that pressure within a system can be used to perform work. For example, in a properly designed system, potential energy of a high pressure container can be extracted by allowing a user to convert potential energy to kinetic energy.
As an example, consider a tank that is under pressure two times atmospheric pressure. The gas will rush out of the tank when a valve is opened until the pressures inside and outside of the tank equalize. Stating this differently, the gas inside the tank expands (from inside to outside the tank) until the pressures equalize. The expansion of the gas can be utilized to perform work.
There have been many engine designs over the years. One design is the Wankel, engine design. The Wankel engine is a four-cycle internal combustion engine that uses a rotating rotor motion instead of reciprocating pistons. The four cycles takes place between a Reuleaux triangle shaped rotor and an epitrochoid-shaped housing.
The housing can be defined as having 360 degrees of rotation. The rotor can generally be described as an equilateral triangle with rounded faces. The sum of internal angles of an equilateral triangle is 180 degrees. In this regard, the rotor revolves around an offset crankshaft wherein the apexes of the rotor contact the housing at all times. An example of this engine 5 design is shown in
A single rotor engine is considered a three cylinder engine. In this regard, the space or volume between the apexes of the triangle and the housing wall define three chambers. Each chamber acts independently of the other chambers and each undergoes the intake, compression, ignition and exhaust cycles of the four-cycle design. Hence, three power cycles are produces by this engine.
The Wankel engine has been modified in many ways. Some modifications of the Wankel design, as well as examples of other designs are illustrated in the following patents and published application.
U.S. Pat. No. 3,426,525 to Rubin is titled Rotary Piston External Combustion Engine.
U.S. Pat. No. 3,509,718 to Fezer et al. is titled Hot Gas Machine.
U.S. Pat. No. 4,206,606 to Reich is titled Rotary Stirling Cycle Engine. It discloses a rotary Stirling cycle machine comprising at least two chambers, said chambers being epitrochoidal in cross-sectional area and having an upper portion, a middle waist portion and a lower portion, with the first chamber mounted to the second chamber in tandem, each chamber having a seal element attached to the waist portion and disposed inwardly, the crank shaft rotatably mounted within the chambers and extending therethrough with the first crank throw portion within the first chamber being 180.degree. out of phase with the second crank throw portion within the second chamber, the first and second rotor elements rotatably mounted on said respective crank throw portions with each rotor element being limicon shaped in circumference and adapted to register with the upper and lower portions of the respective chambers so that the rotor elements cyclically rotate about the rotating crank shaft from a position in registration with the upper portion to a position in registration with the lower portion, said seal elements being in constant sealing engagement with the respective rotor elements to define first cavities in the upper portions and second cavities in the lower portions, and heater-regenerator-cooler means operatively connected to said first and second cavities to condition a working fluid through repeated Stirling cycles.
U.S. Pat. No. 4,357,800 to Hecker is titled Rotary Heat Engine. It teaches a rotary external combustion heat engine for furnishing mechanical energy from a source of heat. The engine includes a ring-like stator having an oval rotor chamber enclosing a cylindrical rotor eccentrically placed within the chamber to define a high displacement high temperature fluid chamber and a lower displacement low temperature fluid chamber. A plurality of extensible vanes extend outwardly from the rotor in sliding contact with the inner surface of the rotor chamber. A source of heat supplies thermal energy to fluid supplied to the high temperature chamber, while a heat sink cools fluid supplied to the low temperature chamber. An economizer heat exchanger is also provided for preheating the working fluid. The relative position of the rotor within the rotor chamber is adjustable for varying the relative displacement of the fluid chambers to control engine working parameters. In another embodiment, a first heat engine is utilized as a motor and is mechanically coupled to a second heat engine utilized as a heat pump for providing an external combustion heat pump or refrigeration unit.
U.S. Pat. No. 4,760,701 to David is titled External Combustion Rotary Engine. The patent describes an external combustion rotary engine comprising a motor member, a free-piston combustion member and a storage tank serving also as a heat exchanger and located between the motor and the combustor. The motor rotors rotate inside an enveloping structure eccentrically with respect to a power shaft to form alternatively compression and expansion chambers. Compressed air produced thereby is ducted first to the storage tank and then to the combustor for burning fuel to produce combusted gases which are in turn ducted to the storage tank where heat is exchanged between the hot gases and the cooler compressed air. The combusted gas is then expanded in the expansion chambers. A fraction of the compressed air is further compressed to a higher pressure level so that it may be used in air pad cushions to isolate the various engine rotating parts from the fixed structures surrounding them. The use of such air cushions prevents contacts between moving parts and eliminates friction, heat production therefrom and wear. The need for lubrication is thus also eliminated. The “externally” performed fuel combustion is much slower than in comparable internal combustion rotary engines. This results in higher combustion efficiencies, lower combustion temperatures and lower rates of production of pollutants such as NO.sub.x.
U.S. Pat. No. 5,211,017 to Pusic is titled External Combustion Rotary Engine. It shows an external combustion rotary engine having a configuration which allows spatial separation of the heaters and coolers, and a process which enables rotary motion of the rotors to be performed without internal combustion. The engine includes the triangular rotors enclosed inside the housings shaped in the form of an epitrochoid curve, the heat generating units, and the heat absorbing and discharging units. The heat generating units and the heat absorbing and discharging units are located outside the housings and connected to the housings. The engine can also include the ultrasonic fuel atomizers inside the heat generating units and the turbine for the purpose of rapid acceleration. The present invention provides the simple, compact, lightweight, extremely energy-efficient and environmentally clean engine.
U.S. Pat. No. 5,325,671 to Boehling is titled Rotary Heat Engine. It describes an engine energized by an external heat source and cooled by an external cooling source, driven by a closed body of gas contained in chambers of variable volume and passages connected thereto, and operating on a Carnot cycle. The apparatus of the engine also has heat pump capabilities.
U.S. Pat. No. 6,109,040 to Ellison, Jr. et al. is titled Stirling Cycle Refrigerator or Engine employing the Rotary Wankel Mechanism. It illustrates a non-reciprocating Stirling-cycle machine which overcomes problems associated with high drive mechanism forces and vibration that seriously hamper reciprocating Stirling-cycle machines. The design employs Wankel rotors instead of the reciprocating pistons used in prior Stirling machines for effecting the compression and expansion cycles. Key innovations are the use of thermodynamic symmetry to allow coupling of the rotating compression and expansion spaces through simple stationary regenerators, and the coordination of thermodynamic and inertial phasing to allow complete balancing with one simple passive counterweight, which is not possible in reciprocating machines. The design can be scaled over a wide range of temperatures and capacities for use as a cryogenic or utilitarian refrigerator or to function as an external heat powered engine.
United States Patent Application Publication 2009/0139227 to Nakasuka et al. is titled Rotary Heat Device. It has a rotary heat engine having a cylinder and a rotor having a rotating shaft rotatably placed in the cylinder. The cylinder has a heat receiving section for supplying heat to the inside of the cylinder and a heat radiating section for radiating heat from the inside. The engine also has an engine section body and an operation liquid storage section. A vaporized gas supply channel and a gas recovery channel communicating with the inside of the cylinder are provided, respectively, on the heat receiving section side and heat radiating section side of the cylinder in the engine section body. The operation liquid storage section is between the vaporized gas supply channel and the gas collection channel in order to aggregate and liquefy recovered gas and is installed such that both channels fluidly communicate with each other. Also, the operation liquid storage section has a heat insulation dam provided with a through hole for preventing backflow of fluid flowing inside.
While each of these devices may be useful for their intended purposes, none show the unique advantages of one embodiment of the present invention.
Specifically none show an engine utilizing an elongated driving force due to opening of a valve when one of three apexes passes a prior exhaust port and the expansion chamber volume is small.
None show that an input valve can be closed at the appropriate timing whereby pressure in the expansion chamber and the pressure in the system outside of the expansion chamber will be approximately equal when the rotor leading apex passes the exhaust port.
Due to the geometry of adding a second inlet and exhaust ports, modified engines suffer from blow-by at certain times. The blow-by occurs as an expansion chamber will be open to both the inlet and exhaust simultaneously. None show the use of valves to prevent blow-by in a system having three apexes of a triangular rotor and two inlets and two exhaust ports spaced about the engine housing.
None show the use of fixed gates mounted in the housing to decrease expansion chamber volume and increase the portion of driving force about one side of a rotor as the rotor orbits about the housing center point.
Another type of design utilizes a linear drive. Some examples include:
U.S. Pat. No. 3,939,719 to Stovall titled An Improved Power Converter Apparatus shows an apparatus for converting the power of a reciprocating member to unidirectional rotation of an output shaft. A reciprocator is connected to a coupling shaft so as to rotate the coupling shaft in alternating directions. Gears and clutches driven by the coupling shaft convert the alternating movement of the coupling shaft to unidirectional rotation imparted to the output shaft. In other embodiments, the reciprocator drives coupling shafts which in turn impart alternating movement to clutch assemblies that cooperate to alternately impart unidirectional rotation to the output shaft.
U.S. Pat. No. 3,973,445 to Ballard titled Conversion Mechanism for Linear to Rotary Motion relates to mechanism for converting linear motion to rotary motion without the use of a crank or crankshaft. Two circular members which may be provided with teeth are driven simultaneously in opposite directions by a chain, belt or rack which is in turn connected to a piston reciprocating in a linear path. The invention is particularly adapted to vapor engines sometimes referred to as expanders. It also comprises both electrically and mechanically actuated valve motions, including a reverse means and means for varying cut-off.
U.S. Pat. No. 4,702,147 to Johnson, et al. titled Engine with Pneumatic Valve Actuation shows an invention providing a valving arrangement for a reciprocating engine in which there are two valve assemblies, each with a pressure responsive valve member. As the piston approaches the end of its stroke in either direction, the exhaust port is closed, such as by an extension on the piston, causing fluid pressure to build up in the end of the cylinder. This pressure is conducted to the valve assemblies through fluid lines, causing the pressure-responsive valve members to move in response to the pressure build-up in the end of the cylinder. These valve members control the inlet and exhaust connections to the cylinder so that the piston is caused to reciprocate by the working fluid as the valve members are moved pneumatically to open and close the lines.
U.S. Pat. No. 5,461,863 to Simonds titled Transducer for Converting Linear Energy to Rotational Energy shows that multiple steam powered cylinders reciprocate to pivot arms back and forth connected to output drive shafts through one way clutches with the output drive shafts being interconnected through gears such that when one shaft is powered, the other is coasting. The inlet and outlet valves for each cylinder chamber are controlled by an actuator which instantaneously snaps the valves between open and closed positions. The power cylinders may be operated individually, in parallel or in series and as required, a valve passageway through the piston may be operated to equalize pressure. A pair of O-rings on the piston engage the cylinder wall only when the adjacent chamber is pressurized, thereby reducing drag in operation of the piston.
While each of these devices may be useful for their intended purposes, none show the unique advantages of another embodiment of the present invention.
None of these patents show an engine with multiple double acting or two way actuators each operable with two one way clutches.
None of these patents show an engine with multiple double acting or two way actuators each being in offset phase of driving force.
None of these patents show a double acting or two way actuator operable with two one way clutches wherein each clutch turns a shaft and the shafts are coupled with a chain to achieve a unidirectional driving force.
Thus there exists a need for a heat engine that solves these and other problems.
In one embodiment of the present invention, it relates to a heat engine having a housing. A generally triangular shaped rotor can drive an offset crank as it eccentrically rotates within the housing. Two inlets with valves and two exhausts are provided. The volume between each face of the rotor and the housing defines three expansion chambers. Six power cycles are provided (one by each expansion chamber times two inlets) per revolution of the rotor. Each valve controls the length of time that high pressure gas is allowed to enter each expansion chamber. The valves are controlled by a processor and close when enough pressure is supplied so that the pressures inside and outside the expansion chamber are equal when the chamber is fully expanded just prior to exhaust. Gates can provide a mechanical advantage to the rotor by reducing the amount of pressure applied to the back side of the fulcrum.
According to one advantage of the present invention, the engine utilizes an elongated driving force due to opening of a valve when one of three apexes passes a prior exhaust port and the expansion chamber volume is small. The faces of the rotor are smooth and undished in order to minimize the volume in each chamber when the valve first opens.
According to another advantage of the present invention, the input valve can be closed at the appropriate timing whereby pressure in the expansion chamber and the pressure in the system outside of the expansion chamber will be approximately equal when the rotor leading apex passes the exhaust port. In this regard, the efficiency of the expansion phase is maximized because all of the energy is utilized as the pressures are equalized when the system opens to the exhaust.
According to further advantage of the present invention, the use of valves prevents blow-by in the system. Blow-by would otherwise occur in a system having three apexes of a triangular rotor and two inlets and two exhaust ports spaced about an engine housing since at times in the revolution of the rotor a chamber would be open to both an inlet and an exhaust port at the same time. Using a valve prevents this occurrence from happening.
According to a still further advantage of the present invention, fixed gates are provided to decrease expansion chamber volume (start of the expansion) and also to increase the mechanical advantage of the rotor during the expansion (the portion of driving force about one side of a rotor as the rotor orbits about the housing center point). The side of the rotor upon which driving force acts is called the positive side of the fulcrum. Further, the undished face allows the gates to fully divide the expansion chambers into two portions due to being able to fully engage the rotor.
The gates can have a selected angular alignment whereby pressure within the expansion chamber acts to force the gates against the rotor face to form a strong seal.
The use of gates also allows the exhaust ports to be moved to different locations about the housing. In one embodiment, the pressure can be applied over about 30 degrees of rotation. However, by adding the gate and moving the outlet, the pressure can be applied over approximately 70 degrees of rotation, greatly increasing the driving force applied to the rotor.
According to a still further advantage of the present invention, the engine has six power cycles per revolution. This is due to three expansion chambers and two inlets. Each power cycle is offset from each other, whereby the combined power curve is smoothed out.
According to a still further advantage of the present invention, a processor is provided to control the opening and closing of the valves. The opening will be at a set point when the volume in the expansion chamber is at or near a minimum. The processor interprets both the input and exhaust pressures and closes the input valve at an exact time which allows for the high pressure gas entering the chamber to fully expand and be approximately equal to the pressure on the low pressure side of the system at exhaust.
According to a still further advantage of the present invention, a partial vacuum can be provided as the gas cools in the condensation chamber. This lower pressure can help to pull to rotor around its rotation.
According to another embodiment of the present invention, it relates to a heat engine having shafts with gears, position gears and a plurality of actuators each having gears. Energy can be harnessed from the first shaft as it rotates. The second shaft can be coupled to the first shaft to transfer energy from the second shaft to the first shaft. One coupler is a chain. Position gears orient the chain wherein the rotation of the second shaft is inverted upon the first shaft so that the first shaft has a constant rotational orientation. Each actuator is preferably a double acting actuator that can supply force to both push and pull upon a belt connected to the actuator rod. A 1-way clutch and gear connects the belt to each shaft wherein the belt (driven by actuator) imparts a positive force upon the first shaft on the out stroke and a positive force upon the second shaft on the return stroke.
According to one advantage of the present invention, the actuators are linear double acting or two way actuators. In this regard, the actuators provide positive pressure in both the extension or out stroke and the retraction or return stroke.
According to another advantage of the present invention, there is preferably a plurality of independent actuators. In this regard, the output power of the engine approaches a relative uniform output.
According to another advantage of the present invention, the timing of the actuators is offset. In a preferred embodiment, the phase timing is calculated as the inverse of the number of actuators. Advantageously, having an offset phase of multiple actuators eliminates a dead spot (when an individual actuator is fully extended or retracted immediately before being energized to move in the opposite direction).
Related, and according to a further advantage of the present invention, a position sensor is provided (and coupled to the belt of the first actuator) so that the position of the actuator is known. Since the timing of each actuator is offset, knowing the position of all actuators is known when the position of any one of them is known (via the processor and encoder).
According to another advantage of the present invention, each actuator is independently energized. In this regard, failure or problems with a single actuator will not directly result in failure or problems with the other actuators.
According to another advantage of the present invention, the actuator cylinder has two ports. Each port has a valve that is closed via a processer at an appropriate time wherein the pressure inside the port equals the pressure outside the port at the end of the stroke. The closing of the valve is determined by the formula P1×V1=P2×V2 wherein P1 is the pressure on the input side of the cylinder, V1 is the volume within the cylinder when the valve closes, P2 is the low pressure on the exhaust side of the cylinder and V2 is the volume of the cylinder when the stroke is complete (fully extended or retracted).
In this regard, the actuator can utilize a full amount of energy (potential energy of expanding gas) in each stroke direction. The valves on the back side of the piston head are open during the actuator stroke to exhaust gas from the cylinder (i.e. first valve open on return stroke and second valve open on extension stroke).
According to a further advantage of the present invention, the output force of the actuators is cumulative. This allows the individual force of each actuator to be extracted even if individually the actuator does not have enough force remaining to rotate a shaft (at or near the end of the stroke).
According to another advantage of the present invention, 1-way clutches are provided. In this regard, the clutches allow force to be transferred from the actuator to a shaft in one direction, and allowed to rotate about the shaft without transferring energy in the other direction. Advantageously, this allows a belt to be used as it imparts a force while under tension and will not need to carry a load under compression.
According to a further advantage of the present invention, position gears are provided to position a chain that couples the shafts. In this regard, the chain can be positioned to invert rotation of the second shaft onto the first shaft. This can be accomplished by going over the top of one shaft and under the bottom of the other shaft, as the shafts rotate in opposite rotational orientations under the push and pull of the actuators. Inversion of the rotational force advantageously allows the first shaft to maintain rotation in a single rotational orientation (unidirectional driving force).
According to a still further advantage yet of the present invention, an engine with multiple double acting or two way actuators each operable with two one way clutches is provided.
According to a still further advantage yet of the present invention, an engine with multiple double acting or two way actuators each being offset in driving force is provided.
According to a still further advantage yet of the present invention, a double acting or two way actuator operable with two one way clutches wherein each clutch turns a shaft and the shafts are coupled with a chain to achieve a unidirectional driving force is provided.
Other advantages, benefits, and features of the present invention will become apparent to those skilled in the art upon reading the detailed description of the invention and studying the drawings.
While the invention will be described in connection with several embodiments, it will be understood that it is not intended to limit the invention to those embodiments. On the contrary, it is intended to cover all alternatives, modifications and equivalents as may be included within the spirit and scope of the invention as defined by the appended claims.
A first embodiment can be viewed by looking at
Looking now to
A high pressure tank 120 is provided. The tank can be any suitable size. The tank 120 can hold a selected amount of working medium 130. The working medium is preferably a commonly available refrigerant that undergoes a phase change between liquid 131 and gas 132 at predictable temperatures and pressures. One preferred refrigerant is R-123. However it is understood that other refrigerants could be used without departing from the broad aspects of the present invention.
A heat source 140 is provided. The heat source 140 is in close proximity to tank 120, whereby the heat source can heat the working medium 120 causing selected amounts of liquid 131 to undergo a phase change to gas 132. The tank can hold the gas at high pressures. It is understood that operating pressures and temperatures are determined based on system requirements and refrigerants used. A gauge 150 is provided for measuring the pressure in the high pressure tank 120.
A high pressure delivery system 160 is provided. The high pressure delivery system 160 can be split into two lines, a first line 165 and a second line 166. The lines are fluidly connected wherein the pressure in each line 165 and 166 are preferably the same. The high pressure delivery system 160 provides high pressure gas to the housing 20 of the engine 10.
A low pressure exhaust system 170 is further provided. The low pressure exhaust system receives low pressure exhaust from the housing 20 of the engine. The low pressure exhaust system has a first line 171 and a second line 172. The first and second lines 171 and 172, respectively, combine in line 173.
The low pressure exhaust 170 goes through a condensation chamber 180 having a heat exchanger 185. The condensation chamber 180 has a gauge to measure pressure within the system on the low pressure side of the system. The condensation chamber 180 empties liquid condensate into a low pressure condensation tank 200. From there, a pump 210 is used to route liquid 131 back into the high pressure tank 120 to repeat the cycle. Looking briefly at
A processor 230 is provided. The processor 230 communicates with position sensors or locators 240 and 241 (which monitor the location of the rotor 60 within the housing 20). The processor 230, as seen in
Turning now to
The housing 20 has a wall 21 with an inside surface 22. The inside surface defines a general epitrochoid shaped structure having a first section 23 and a second section 24. The sections are generally open to each other, but have a first radius 30 and second radius 35 there between. The radii 30 and 35 protrude a small amount toward the center of the housing 20. The radii 30 and 35 have openings or recesses 31 and 36 respectively, to accommodate stationary gates (described below). The openings preferably span from the top to the bottom or the full dimension of the housing and are complimentary in shape to the respective gates. It is appreciated that the openings or recesses may not span the full dimension so long as they support gates that do span the entire dimension.
The housing has an inlet 40 with a valve 41, an inlet 45 with a valve 46, an outlet 50 and an outlet 55. The inlets 40 and 45 are spaced apart (preferably approximately 180 degrees on separate sides of the housing) and are separated by outlets 50 and 55. The valves 41 and 46 are preferably selectably opened and closed under the direction of the processor 230 based on the location of the rotor 60 within the housing 20.
The rotor 60 is generally reuleaux shaped. In this regard, the rotor 60 has three faces, namely a first face 65, a second face 66 and a third face 67. The faces meet at apexes, namely the apex A 70, apex B 71 and apex C 72. Seals 75, 76 and 77 are provided respectively at apex A 70, apex B 71 and apex C 72. The rotor 60 is shown prospectively in
It is understood that the seals actually contact the housing, but for sake of simplicity in description, it is described herein as apex's passing certain points such as inlets and exhausts.
As is best seen in
A first expansion chamber 90, a second expansion chamber 100 and a third expansion chamber 110 are provided. The expansion chambers are located between the rotor 60 and the housing 20. A driving force is provided in an expansion chamber due to the offset orientation of the fulcrum and the rotor center.
It is understood, looking at
A gate 250 is provided and shown in
A gate 260 is further provided. Gate 260 is identical to gate 250. Gate 260 is removably received within opening 36.
As seen in
An alternative gate 450 is illustrated in
Gate 460 can be provided and is similar to gate 450.
It is understood that the portions of the gates within the housing are movable. It is preferred that the gates are movable from a first gate position wherein the gate is flush with the housing wall to other positions wherein the gate either contacts the rotor or is projected into an expansion chamber without contacting the rotor. The gates preferably are operable to rotate in the same direction as the rotor. This allows pressure to press the gates against the rotor, as well as allowing the rotor to slide over the gates.
As seen in
V1 is that volume occurring when an inlet valve opens. This occurs when the leading apex passes an inlet and the trailing edge passes an exhaust.
V2 occurs when the rotor advances a sufficient amount to a maximum efficiency point. The maximum efficiency point occurs when the input valve closes at a volume so that the high pressure gas entering the expansion chamber is allowed to fully expand and be equal to the pressure on the low pressure side of the system when the leading apex reaches the exhaust port and the volume is at V3.
It is appreciated from studying of the above-chart that there are six power cycles per revolution of the rotor 60 within the housing 20.
As means of an example only, at V2, the volume can be 1 unit and the pressure 4 units. Then, at V3, the volume can be 4 units and the pressure 1 unit Likewise, the pressure external of the expansion chamber is 1 unit. In this regard, the pressure inside and outside of the expansion chamber are equal at V3. The timing of the opening and closing of the input valves is determined by the processor whereby this result is achieved.
Turning now to
Turning now to
Also, the gates allow the exhaust to be much closer to the next successive inlet, as the gate prevents back-flowing within an expansion chamber as it bifurcates the expansion chamber. The inlet valves can also be opened earlier in the cycle thereby elongating the driving force. In this regard, in an embodiment without a valve, the inlet valve can be opened with the trailing apex passes the exhaust port. However, when a gate is provided, there is no way for the gas to reach the exhaust port and the valve can be opened before the trailing apex passes the exhaust port.
Looking now at
It is appreciated that the engine 10 of the present invention is able to power many types of devices. Two examples are as an automobile engine and as a means to extract energy out of an existing heating system such as a building heating system.
One typical building heating system is a furnace. In this regard, the current furnace simply burns fuel and uses the waste heat to warm a building. By installing a heat engine, the fuel would still be burned, but the heat energy from said burning is used to propel the heat engine, such as the heat engine of the present invention, which can be used to generate electric power via generator.
The waste heat contained in the gas exiting the exhausts is still routed through the condensation chamber 180. Yet, heat exchanger 185 can be used to draw heat from the condensation chamber 180 and transfer it to a building via the building HVAC system. In this regard, the heat of the exhaust gas is not lost, and not dissipated generally. Instead, the dissipated heat is redirected to the building to fulfill the environmental requests of the HVAC system.
Another embodiment is illustrated in
Looking first at
A valve is shown generically in
It is appreciated that while these above-mentioned components are shown and described, that alternatives and substitutions may be made without departing from the broad aspects of the present invention, and specifically the broad aspects of the engine 750 as it is described below.
Turning now to
Each of these components is described below in detail. A processor 755 is provided and is not described in detail below. However, the processor controls the opening and closing of the valves.
Base 760 is shown in
Turning now to
A second shaft 780 is also provided. The second shaft 780 has two ends and is rotatable about an axis of rotation 781. A gear 782 is at the second end of the shaft 780. The gear 782 is preferably fixed to the shaft 780 such that the rotation of the shaft causes the gear to rotate in a likewise manner.
Shafts 770 and 780 are preferably parallel to each other. In this regard, the axis of rotation 771 of shaft 770 is parallel to but offset from the axis of rotation 781 of shaft 780.
A positioning gear 790 and a positioning gear 800 are also provided and are supported by the base 760. Gear 800 is preferably fixed relative the base 760. However, a slot 791 is provided so that gear 790 is adjustable supported relative the base. The slot is preferably oriented towards and away from the center of the second positioning gear 800 so that the first and second positioning gears 790 and 800 can be moved closer to and further away from each other to provide tension to the chain.
A chain 810 having an inside 811 and an outside 812 is further provided, and is best seen in
Looking now at
Actuator 820 has a cylinder 825. The cylinder 825 has two ends. A port 830 operable with a valve 831 is at the first end. A port 840 operable with a valve 841 is at the second end. Valves 831 and 841 can be selectably opened and closed to allow high pressure gas to enter the cylinder and drive a rod 850 by acting on a selected side of a head or boss 851. In this regard, when pressure is introduced on the first side of the head 851 the rod extends, and when pressure is introduced on the second side of the head, the rod retracts. A clamp 855 is provided on the outer end of the rod 850. The clamp 855 is used to connect the rod to a belt 860.
A position sensor 865 is provided and communicates the location of the belt 860 to a controller. In this regard, the timing of the actuator 820 can be monitored and maintained. Position sensor 865 fits within the grooves on the inside portion of the bottom of the belt. Sensor 865 communicates with an encoder to determine the position of the head of the actuator and communicates the information to the processor 755.
A gear 870 with a perimeter 871 is provided. The gear has a clutch bearing 872. Clutch bearing 872 is preferably a 1-way clutch bearing that is press fit securely within gear 870. Gear 870 is attached to shaft 770. The gear, via the clutch bearing 872, locks in one direction wherein it will cause the shaft to rotate, yet turns freely in the opposite direction without imparting a force onto the shaft.
A second gear 880 also with a perimeter 881 and a clutch bearing 882 is provided. Gear 880 is attached to shaft 780. The second gear is similar in operation to the first gear.
Belt 860 is preferably wrapped about gears 870 and 880. The belt rotates in a first direction about gears 870 and 880 when the rod 850 is extending from the cylinder 825. The belt rotates in the opposite direction about gears 870 and 880 when the rod is retracting into the cylinder 825. Clutch bearings 872 and 882 are 1-way clutch bearings. In this regard, the bearings can affect rotation of respective shafts in one direction yet freely rotate about the respective shaft when rotating in the opposite direction. Specifically, during the extension phase, gear 870 causes shaft 770 to rotate while gear 880 is not engaged with shaft 780. Yet, during the retraction or return phase, gear 880 engages and causes shaft 780 to rotate while gear 870 is disengaged with shaft 770.
Looking now to
The return or retracted stroke is illustrated in
The closing of the valves is preferably determined to be to point where the pressure inside and outside of the cylinder are equal at the end of the stroke. The closing of the valves is driven by a processor 755 that interprets the following formula: P1×V1=P2×V2. Where:
P1=High pressure on the input side of the engine.
V1=The volume within the driving side of actuator when input valve closes.
P2=Low pressure on the Exhaust side of the engine.
V2=The full volume within the driving side of the actuator when the stroke is completed.
Looking now to
The second, third and fourth actuators are similar to the first actuator, and are briefly described below. Then, following this brief description, independent operation of the four actuators is shown and described.
Actuator 920 has a cylinder 925 with two ends. A port 930 with a valve 931 is at the first end, and a port 940 with a valve 941 is at the second end. A rod 950 with a head 951 can be extended from and retracted into the cylinder 925 under operation of the valves. A clamp 955 connects the end of the rod 950 to a belt 960. The belt 960 operates gears 970 and 980 driving shafts 770 and 780, respectively.
Actuator 1020 has a cylinder 1025 with two ends. A port 1030 with a valve 1031 is at the first end, and a port 1040 with a valve 1041 is at the second end. A rod 1050 with a head 1051 can be extended from and retracted into the cylinder 1025 under operation of the valves. A clamp 1055 connects the end of the rod 1050 to a belt 1060. The belt 1060 operates gears 1070 and 1080 driving shafts 770 and 780, respectively.
Actuator 1120 has a cylinder 1125 with two ends. A port 1130 with a valve 1131 is at the first end, and a port 1140 with a valve 1141 is at the second end. A rod 1150 with a head 1151 can be extended from and retracted into the cylinder 1125 under operation of the valves. A clamp 1155 connects the end of the rod 1150 to a belt 1160. The belt 1160 operates gears 1170 and 1180 driving shafts 770 and 780, respectively.
Turning now to
The actuators apply positive force to shaft 770 during the extension stroke and apply positive force to shaft 780 during the return stroke. The forces applied are cumulative to the pressure within the respective cylinder.
It is appreciated that the rotational force of the shafts 770 and 780 is perpendicular to the extension and retraction force of the actuators. The belts driven by the respective actuators are preferably offset from the center of the shafts by about 2.25 inches. Of course, the offset can vary depending on the size of the cylinders and other components. The preferred (but not limited) offset is between 1 and 12 inches. Yet, this amount could be more or less without departing from the other aspects of the present invention.
Rotational energy from shaft 770 can be used for any number of purposes, including being connected to a generator to produce electricity. Given the operable connection between the shafts and the use of 1-way clutches, it is appreciated that the force of the actuators is cumulative from the engine 750. The force output in one embodiment is shown in chart and data form in
It is thus seen that the actuators independently follow the formula P1 times V1 equals P2 times V2 in harvesting potential energy from the actuator. The output from each actuator is cumulative with the output of the other actuators.
Thus it is apparent that there has been provided, in accordance with the invention, a heat engine such as a linear drive heat engine that fully satisfies the objects, aims and advantages as set forth above. While the invention has been described in conjunction with specific embodiments thereof, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art in light of the foregoing description. Accordingly, it is intended to embrace all such alternatives, modifications, and variations as fall within the spirit and broad scope of the appended claims.
This United States utility patent application claims priority on and the benefit of provisional application 61/772,740 filed Mar. 5, 2013, the entire contents of which are hereby incorporated herein by reference. This patent application is a continuation-in-part application of application Ser. No. 13/469,306 filed on May 11, 2012, which itself claims priority on and the benefit of U.S. provisional application 61/485,849 filed May 13, 2011, the entire contents of both being hereby incorporated herein by reference.
| Number | Date | Country | |
|---|---|---|---|
| 61772740 | Mar 2013 | US | |
| 61485849 | May 2011 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 13469306 | May 2012 | US |
| Child | 14193247 | US |
