FIELD
The present invention relates generally to a fluid pumping or fluid compression engine, such as utilizing an internal homogeneous-charge combustion ignition (HCCI) free-piston engine design. Such a fluid pump or compressor is capable of producing compact fluid power for applications requiring mobility.
BACKGROUND
There is a need for compact fluid pumps and compressors in fields such as orthotics, power tools, and robots. Applications in such fields require portable power to pressurize or compress fluid. For example, power tools may include pneumatic nail guns, branch clippers, garden pruners, or load lifting assistants. Such portable power is commonly derived from an electrical air compressor powered by a battery. However, the weight and energy density of the battery often limit portability. As an alternative, an internal combustion (IC) engine can be used as a compressed fluid power source in such applications. Compared to a battery, a miniaturized combustion engine can provide higher power density and higher energy density.
However, IC engines are difficult to miniaturize to sizes below approximately 10 cm3(cubic centimeters). Challenges in miniaturizing existing IC engines to a small size include fabrication, control, friction, and blow-by leakage. For example, a four-stroke IC engine is difficult to fabricate at a miniature scale due to additional features such as a camshaft, valves, and rocker arms. As another example, in a two-stroke IC engine, spark plugs, fuel injectors, and various sensors are all difficult to miniaturize in order to operate in a small engine.
An alternative configuration involves homogeneous-charge combustion ignition (HCCI) engines. Such engines typically use a crankshaft. These engines also utilize active control schemes comprising mounted sensors and an actuator to regulate rebound, spark ignition or diesel compression ignition, and proper alignment. Due to the complexity of such a configuration and the need for a crankshaft, miniaturizing a full-scale HCCI crankshaft engine would be difficult.
Yet another alternative configuration utilizes a free-piston engine. A free-piston engine is a type of internal combustion engine not having a crankshaft. Without a crankshaft, this configuration is more compact and simpler than some other configurations. However, free-piston engines are difficult to regulate requiring active controls to regulate piston motion. Incorporating active control schemes at a miniature scale presents difficulties, especially given the limited space available in a miniature engine.
Another configuration involves glow plug ignition engines used in applications such as model aircraft to power a fluid compressor. Such engines are small in size and utilize glow plug ignition, wherein a glowing hot platinum wire is used in the combustion chamber to ignite the fuel air mixture through its thermal energy and catalytic effect. The problem with this engine configuration is low thermal efficiency caused by a slow combustion process. Furthermore, the use of a glow plug in this configuration limits further miniaturization.
Because of the inherent challenges in miniaturizing existing engine configurations, it would be beneficial to develop an engine that can be fabricated at a miniature scale, operate with reasonable power for portable use, and have a high enough power-to-weight ratio to be effective in orthotics, power tool, and robotics applications.
SUMMARY
A system for providing pressurized and/or compressed fluid comprising a fluid pump/compression cylinder, coupled to a combustion cylinder and a rebound chamber, and a piston assembly contained at least partially and capable of movement within the combustion cylinder and the fluid pump/compression cylinder, wherein the combustion cylinder comprises a holding chamber and a combustion chamber, and wherein the holding chamber and the combustion chamber may be connected by at least one port, and wherein the fluid pump/compression cylinder comprises a pump/compression chamber, and wherein the rebound chamber comprises a rebound system, and wherein the pump/compression chamber may comprise at least one inlet and at least one outlet.
FIGURES AND TABLES
FIG. 1 is a schematic diagram of an exemplary embodiment of the engine being used in conjunction with an orthotic leg/foot apparatus.
FIG. 2 is a schematic diagram of the exemplary embodiment of the engine of FIG. 1 being used in conjunction with an orthotic leg/foot apparatus as provided to a person's leg and foot.
FIG. 3 is a schematic diagram of an exemplary embodiment of the present invention showing an exterior of an engine cylinder.
FIG. 4 is schematic cross-sectional view of an engine cylinder according to an exemplary embodiment of the present invention.
FIG. 5 is schematic cross-sectional view similar to FIG. 4, but at an angle from the top of an engine cylinder according to an exemplary embodiment of the present invention.
FIG. 6 is a schematic cross-sectional view of a cylinder at a certain stage in the combustion cycle according to an exemplary embodiment of the present invention.
FIG. 7 is a schematic cross-sectional view of a cylinder at a different stage that in FIG. 6 in the combustion cycle according to an exemplary embodiment of the present invention.
FIGS. 8-10 are schematic cross-sectional views showing scavenging flow patterns.
FIG. 11 is a schematic diagram of a piston assembly, seal, and spring according to an exemplary embodiment.
FIG. 12 is a schematic diagram of the piston assembly, seal, and spring of FIG. 11 but shown from a angle to the side.
FIG. 13 is a schematic diagrams of an engine cylinder showing a slot for a starting element provided in a compression cylinder according to an exemplary embodiment.
FIG. 14 is an enlarged portion of the view of FIG. 13 showing the slot, a starting element and an absorption element at the end of the slot.
FIG. 15 is a schematic diagram of a valve according to exemplary embodiment of the present invention.
FIG. 16 is a schematic diagram of another valve according to exemplary embodiment of the present invention.
FIG. 17 is a schematic diagram of yet another valve according to exemplary embodiment of the present invention.
FIGS. 18-25 are graphical representations representing data from various experiments related to the performance of a free piston engine design of the present invention.
FIG. 26 is a perspective view of an exemplary embodiment of an engine design according to the present invention.
FIG. 27 is a perspective view in cross-section of the exemplary embodiment of an engine design of FIG. 26 and according to the present invention.
FIG. 28 is a schematic diagram of the energy balance of an engine according to an exemplary embodiment of the present invention.
DESCRIPTION
Small, light-weight portable engines producing compressed fluids are capable of use in applications such as orthotics, power tools, and robots. An example of such an engine is shown in FIGS. 1A and 1B, where the engine provides compressed fluid to power an orthotic leg/ankle system that may assist for example injured or disabled persons in walking. FIGS. 1 and 2 show the engine 10 attached to the back of the orthotic leg/ankle system 11. According to a preferred embodiment, the engine 10 uses a liquid fuel and is free of external electric power cords and heavy electric batteries that could limit portability.
Designs according to the present invention are useful for compressing fluid, such as gases including air, as well as for hydraulic pumps, wherein non-compressible fluids, such as certain liquids, are pressurized and accumulated so as to generate hydraulic power, or as for alternator designs, wherein linear motion is converted to electrical energy, to generate electricity. The uniqueness of the designs of the present invention is based upon the extraction of work from linear motion of one or more pistons, as opposed to the extraction of work from rotary shaft output. As a result, piston pneumatic pumps, hydraulic pumps and alternators are contemplated applications for small engines of the present invention. For purposes of describing certain preferred embodiments of the present invention with the understanding that engines of the present inventions can be used as stated above, a fluid compression apparatus is described as follows.
Referring to FIG. 3, an engine cylinder is shown comprising a combustion cylinder 12 and a compression cylinder 14, which components may be made integrally or as separate components and connected together. The engine cylinder also comprises a fuel inlet 16, an exhaust outlet 18, a fluid inlet 20 and a compressed fluid outlet 22, as are shown. The engine cylinder may comprise a metal alloy (such as an aluminum alloy) or other suitable materials.
As shown in FIGS. 4 and 5, the combustion cylinder 12 may comprise a combustion chamber 24 and a holding chamber 26. The combustion cylinder 12 is shown as comprising an outer cylinder 28 and a cylinder liner 30. The cylinder liner 30 may comprise metal or metal alloys (e.g. steel, titanium or brass), layered metals (e.g. chrome-coated brass, anodized aluminum, or other electroplated metals), polymer-coated materials (e.g. polytetrafluoroethylene (PTFE, e.g. Teflon®) coated metals), or ceramic or ceramic-coated (e.g. diamond coated) materials or other suitable materials. A piston assembly 31 is illustrated comprising a piston rod 32, connected on one end to a combustion piston-head 34 and on the other end to a compression piston-head 36. Also, a rebound element 38 is shown located within the cylinder. As shown, one end of the piston assembly extends into and through the holding chamber and further into the combustion chamber. The combustion piston-head 34 is shown located inside the combustion cylinder. Piston and rod connection techniques including wrist pins and the like are well known and any such connection is contemplated. According to a preferred embodiment, as shown in FIGS. 3-7, the piston assembly 31 comprises a free piston assemble, i.e., the piston assembly 31 is not connected to a crankshaft so as to provide linear output, i.e. compression or fluid pumping from the compression cylinder 14.
In some embodiments, the piston assembly 31 may also comprise a starting element 40. According to exemplary embodiments as illustrated, the starting element 40 comprises a starting handle for manual starting, but could otherwise comprise a compressed fluid starter, an electromagnetic starter, a spring-loaded starter, or otherwise. The purpose of the starting element is to cause at least one compression of fuel/air mix within the combustion chamber 24 so as to allow for a first combustion within the combustion chamber 24 to drive the piston 34 and thus piston assemble 31 away from the end of the combustion chamber 24.
The combustion cylinder 12 also comprises the inlet 16 as such can be operatively connecting a fuel source (e.g. a carburetor or a fuel injector system). The inlet preferably opens into the holding chamber 26. It accordance with a preferred embodiment, the holding chamber 26 is connected for fluid communication to the combustion chamber 24 by way of a passage 42 that opens into the combustion chamber 24 at a determined position (discussed more below) by way of a port 43. The passage 42 may comprise a space provided along and within the wall of the combustion cylinder liner 30 to fluidly connect the combustion and holding chambers 24 and 26. For example, the space may be created by removing material from the combustion cylinder liner 30. The combustion cylinder 12 also comprises the outlet or exhaust 18 for connecting the combustion chamber 24 to a space outside the combustion cylinder. In an exemplary embodiment, the space outside the combustion cylinder 12 is an exhaust system.
The compression cylinder 14 comprises a compression chamber 44 with the compression cylinder shown as connected to one end of the combustion cylinder 12. According to an preferred embodiment, the compression cylinder 14 may also comprise an outer cylinder 46 and a cylinder liner 48. The cylinder liner may comprise metal or metal alloys (e.g. steel, titanium or brass), layered metals (e.g. chrome-coated brass, anodized aluminum, or other electroplated metals), polymer-coated materials (e.g. PTFE coated metals), or ceramic or ceramic coated (e.g. diamond coated) materials, or other suitable materials. Alternatively, the compression cylinder 14 may also comprise glass or polymeric materials (e.g. PTFE). A seal 50 (described in greater detail below) is preferably located at one end of the combustion cylinder 12, forming a boundary between the holding chamber 26 and another chamber, such as the compression cylinder or another (intermediate) chamber (e.g. the rebound chamber). As shown in FIGS. 4 and 5, the seal 50 preferably includes a plurality of disc-like elements 52 that are supported in position by being sandwiched between the ends of the combustion cylinder 12 and the compression cylinder 14. As shown in FIGS. 11 and 12, these discs 52 are slotted as shown at 53 so as to allow for passage of the piston rod 32 as it is movable back and forth. By using plural discs 52, an effective boundary can be provided to the holding chamber 26 so that inlet gas/air mixture or other combustible fuel does not flow into the compression cylinder or any of its chambers. The slots 53 are preferably tightly fit to the piston rod's 32 diameter to minimize leakage. The pistons are rigidly connected so as to move together. The result is a holding chamber 26 sealed on the one side bounded by the seal 50 that varies in volume with movement of the combustion piston 34 without regard to the movement of the compression piston 36.
Referring again to FIGS. 4 and 5, according to a preferred embodiment, the piston assembly 31 extends into the compression chamber 44. The piston assembly 31 is also shown extending into and through a rebound chamber 54. The compression piston-head 36 is positioned to be located inside the compression cylinder 14. The compression cylinder 14 also preferably comprises the fluid inlet 20 and the compressed fluid outlet 22. The fluid inlet 20 can thus connect the compression chamber 44 to a space outside of the compression cylinder 14. For example, the space outside of the compression cylinder 14 may be the environment. According to an embodiment of the present invention, the compressed fluid outlet 22 may connect the compression chamber 44 to a compressed fluid storage system, for example an accumulator, schematically shown in FIGS. 4 and 5. Many types of fluid accumulators are well-known, and any of such accumulators could be used in accordance with the present invention.
As shown in FIGS. 4 and 5, according to a preferred embodiment, the compression cylinder 14 also comprises the rebound chamber 54. According to any exemplary embodiment, the rebound chamber 54 also comprises an elastic rebound element 38 (e.g. an element that does not experience permanent deformation when compressed). For example, the rebound chamber 54 may house a spring as the rebound element 38 that may comprise a coil spring, a wave spring, or another embodiment to store and return sufficient energy. The spring may comprise metal or metal alloys (e.g. steel, titanium or beryllium) other suitable materials. Alternatively, the rebound element may be configured as a system, such as a pneumatic, electrical, magnetic, or hydraulic system. According to alternative embodiments, the rebound element can be housed in either of the holding chamber 26 or the compression chamber 44. According to a preferred embodiment as illustrated, the rebound element 38 of a compressive type can be located within the rebound chamber 54. According to a preferred embodiment, the rebound chamber 54 and the rebound element 38 may be located between the seal 50 and the compression piston-head 34, as seen in FIGS. 4 and 5. More specifically within the illustrated embodiment, the spring as the rebound element 38 sits against a seat portion 58 (see FIGS. 11 and 12) of the manual start element 40 and against the internal edge of the compression cylinder sleeve 48 so as to provide an effective bias to the start element 40, which is fixed with the piston rod 32 for axial movement thereof along with the combustion piston 32. According to an alternative embodiment, one end of a spring may be attached to the piston rod 32.
As shown in FIG. 6, according to an embodiment of the present invention, the engine may comprise a two-stroke engine utilizing a scavenging process allowing exhaust to exit while a fuel mixture enters the combustion chamber 24. As the piston assembly 31 moves away from the combustion end of the cylinder, the exhaust outlet may be exposed to the combustion chamber 24, letting out the exhaust, slightly before the fuel inlet port 43 is exposed, letting in the fuel mixture and allowing for the completion of the scavenging process. The fuel mixture may comprise a fuel (e.g., a hydrocarbon mixture, such as diesel fuel, an alcohol, such as methanol, or another gaseous or liquid fuel, such as dimethyl ether) and a source for oxygen (e.g. air). The fuel mixture may also comprise a lubricating agent, such as oil or other suitable lubricant. According to an exemplary embodiment, the fuel mixture may comprise, as necessary, between 1 and 20 percent lubricating agent. In alternative embodiments, other methods to lubricate the engine may include utilizing a separate lubricant reservoir, lubricant dripping, or lubricant impregnated materials. In embodiments utilizing fuel injection methods, the oxygen source may enter the combustion chamber through an inlet valve.
Referring again to FIG. 6, according to the illustrated embodiment, movement of the piston assembly toward the compression end causes the compression piston-head 36 to compress fluid within the compression chamber 44, which in turn causes positive pressure to build-up in the compression chamber 44. The compressed fluid may then be let out of the compression chamber 44 through the fluid outlet 22, which may be regulated by a compressed fluid outlet valve or the like. The movement of the combustion piston-head 36 toward the compression-end of the cylinder also causes a compression of the rebound element 38 for example by causing the compression spring to be compressed, as shown in FIG. 6.
According to the exemplary embodiment as shown in FIG. 7, approximately at the time the piston assembly 31 begins to move back toward the combustion-end of the cylinder, a homogenous or near homogeneous fuel-oxygen mixture is preferably initiated so as to enter through the fuel inlet 16 into the holding chamber 26. The fuel inlet 16 may be regulated by a fuel inlet valve or the like as are conventionally known. According to an exemplary embodiment, the fuel inlet valve may comprise a reed valve or other method wherein the fuel inlet 16 and outlet 18 for exhaust valves are exposed to the combustion chamber 24 at the appropriate time. In alternative embodiments, a fuel inlet valve and the outlet for exhaust may be controlled electronically and may comprise a sensor assembly. As the piston assembly 31 begins to move toward the compression-end of the engine, the combustions piston head 34 begins to pressurize the fuel mixture while the piston head 34 is still blocking the mouth(s) of the port(s) according to an embodiment. Further movement of the piston assembly toward the compression end (as seen FIG. 6) exposes the port 43 of the passage 42 and the outlet 18 for exhaust, allowing the positive pressure of the fuel mixture to cause the mixture to enter the combustion chamber 24 from the holding chamber 26 and through the passage 42 and out the port(s) 43 so as to also simultaneously force the exhaust out of the combustion chamber 24 through the outlet 18 for exhaust. According to alternative embodiments, fuel and/or a source for oxygen may be injected directly into the combustion chamber 24 (e.g. direct injection). Alternatively, fuel and/or a source for oxygen may be separately introduced.
As shown in FIG. 7, according to the illustrated embodiment, the compressed rebound element 38 (e.g. spring) will exert a biasing force causing the piston assembly 31 to move (i.e. return) toward the combustion-end of the cylinder. The movement of the compression piston-head 36 away from the compression end may lower the pressure in the compression chamber 44 due to the simultaneous or nearly simultaneous closing of the fluid outlet valve 22. As the compression piston head 36 moves, fluid (e.g. air) may enter through the fluid inlet 20, which may be regulated by a fluid inlet valve, into the compression chamber 44.
The movement of the piston assembly 31 toward the combustion-end of the cylinder (as seen in FIG. 7) will eventually effectively block the port 43 of passage 42 and the exhaust outlet 18. According to a preferred embodiment, the movement of the piston assembly 31 may continue until the fuel-oxygen mixture reaches a compression corresponding to sufficient pressure and temperature, to cause ignition of the charge and initiating combustion. The force of combustion may cause positive pressure to build-up in the combustion chamber pushing the piston assembly 31 toward the compression-end of the cylinder.
As shown in FIGS. 8-10, the combustion cylinder 12 may comprise one or more ports, which ports would include an inlet 43 (as the port opening directly into the combustion chamber 24) and an outlet or exhaust 18 (as a portion opening directly from the combustion chamber 24). The ports may be configured to enable scavenging, such as cross-flow scavenging, uni-flow scavenging, or loop-flow scavenging (also known as Schnuerle type scavenging). According to an exemplary embodiment, the combustion cylinder 12 comprises the two or more ports as shown in FIGS. 8-10 in a configuration taking advantage of loop-flow scavenging. As shown in FIG. 9, the mouths of the ports 43 and 18 can be positioned such that the inlet flow is directed away from the exhaust outlet such that the gases initially enter a combustion chamber 24 moving away from the exhaust outlet 18. As shown in FIG. 10, the configuration may comprise three (or more) ports 43 wherein the port 43 located opposite the exhaust outlet 18 in the combustion chamber 24 is also directed away from the exhaust outlet 18.
As shown in FIGS. 11 and 12, the piston assembly 31 may comprise a piston rod 32, connected on one end to a combustion piston-head 34 and on another end to a compression piston-head 36, and a compression element as a rebound element 38. According to an exemplary embodiment, the compressing element 38 is at least partially provided inside the compression cylinder 14 above the compression piston-head 36. The piston assembly 31 may comprise one or more wrist or other type pins attaching the piston-heads to the piston rod 32. The piston rod 32 may comprise one or multiple diameters throughout its length to accommodate assembly, for example, to accommodate the diameter of the pin used to attach a piston-head to the piston rod 32. The combustion piston head 34 may be comprised of metal (e.g. titanium, steel, or aluminum), metal alloys, or metal mixtures. The compression piston head 36 may also be comprised of metal or metal alloys (e.g. titanium, steel, or aluminum), polymeric materials (e.g. PTFE, nylon, or other polymers)), ceramic materials, graphite, or other suitable materials.
Multiple variables, such as the operating frequency, affect the efficiency and the output power of the engine. The power output of the engine can be adjusted to accommodate the requirements of the planned end-use application. For example, a 10 W output may be appropriate for an orthotic appliance, whereas a lift-assist application may require a power output as high as 100-200 W. To achieve the desired power output, the frequency of the engine can be adjusted by the selection of the materials and construction of the piston assembly and the rebound element. Also, the frequency and the displacement may be varied. For example, the material and dimensions of the piston heads and piston rod may be chosen to reach a suitable weight relative to the stiffness (i.e. the spring constant or spring rate) of the rebound element (e.g. spring). On the other hand, a suitable rebound element may be chosen to match the weight of the piston assembly and to achieve an optimal rebound effect. For example, a rebound element that is too stiff will absorb too much of the energy created by combustion, thus lowering the output power of the engine. A rebound element that is not stiff enough will have difficulty returning the piston assembly back into position to pressurize and ignite the fuel, thus causing poor or incomplete combustion. According to a preferred embodiment, the rebound effect causes sufficient compression of the fuel-oxygen mixture to ignite the mixture without the use of another source of ignition, such as a glow plug or a spark plug. An optimal operating frequency will minimize leakage and friction, and maximize compressed fluid output power. Other materials (e.g. for the engine cylinders) may be chosen keeping in mind the desired portability and light weight. For example, according to a preferred embodiment, the engine cylinders may comprise aluminum or aluminum alloys, as opposed to heavier metals.
The seal 50, for example, can comprise a double jaw seal, as such may be used to isolate the holding chamber 26 from the rebound chamber 54. The seal configuration is preferably chosen so that it fits tightly around the piston rod 32 while permitting the piston rod to slide along the slots 53 and the seal 50 effectively prevents a substantial amount of fuel-oxygen mixture from escaping from the holding chamber 26 into another area, for example, a rebound chamber or a compression chamber. The seal 50 may comprise multiple elements 52, as described above, with each element 52 made up of polyether ether ketone (PEEK), bronze, PTFE, or other suitable material or combination of materials. The efficiency of the seal 50 affects the leakage of fuel from the holding chamber 26. A tighter, more efficient seal will improve (i.e. lessen) leakage and advantageously allow for smaller bore-size engines (e.g. a few millimeters or micro- or nano-scale engines) to be operational.
As shown in FIG. 13, the starting handle element 40 may extend through an axially extending slot 60 provided along a wall of the compression cylinder 14 according to an exemplary embodiment. In alternative embodiments, another method of initially displacing the piston assembly may be used such that a starting handle may not be required. FIG. 14 shows an alternative embodiment of the slot 60 comprising a means, such as a rubber bumper 62 for preventing impact (e.g. a spring, air chamber, or the like) positioned to prevent the starting handle element 40 from impacting the cylinder wall at the end of the slot.
According to exemplary embodiments, many different types of valves may be chosen for the various inlets and outlets. For example, stacked valves shown in FIGS. 15 and 16 can be chosen to control the flow of compressed fluid from the device. Such a stacked valve construction can be designed based upon well-known and conventional techniques where the stacked elements together control the fluid flow from the device outlet. As shown in FIG. 17, the valve at the fuel inlet may be a Reed-type valve according to an exemplary embodiment, as Reed valves themselves are well known. The valve may comprise metal or metal alloys, such as stainless steel, steel, titanium, or other suitable materials.
EXAMPLES
A number of experiments were conducted to study the construction and operating parameters of engines in accordance with the present invention. The experiments were conducted either by utilizing various computerized models, or by studying prototypes of engine designs.
In the first example, engine blow-by leakage was modeled and compared against experimental data utilizing a small glow-plug engine. As shown in FIG. 18, simulation data of heat transfer alone and heat transfer and leakage were compared to experimental data measuring motoring peak pressure. Results from the model and experimental data show that motoring peak pressure increases with engine speed, as measured by rotations per minute, indicating that miniature engines can be run at high speed to avoid excessive blow-by leakage.
In another example, engine leakage and friction efficiencies were modeled in combination to determine optimal engine speeds (i.e. frequencies) as shown in FIG. 19. High engine speed may reduce leakage and heat transfer losses but may increase friction loss. Considering these two factors, optimal operating ranges were approximately between 100 and 150 Hz. Along with knowledge of a target engine output power, engine speed assists in determining the appropriate engine size.
In the third example, the combustion cylinder pressure, piston position, compressed air reservoir pressure, engine frequency and indicated mean effective pressure (IMEP) were modeled using a computer model and a glow ignition prototype engine (a remote-control-aircraft engine) to estimate the compressed fluid power output of the engine. As shown in FIG. 20, the combustion chamber pressure built up from about 15 bar to about 20 bar and above after the piston movement began to expose the exhaust outlet to the combustion chamber and scavenging occurred, supplying the engine with fresh fuel-oxygen mixture for the next cycle, thus increasing the pressure. As shown in FIG. 21, pressure in the compressor chamber rose with operating time as pressure in the reservoir attached to the compressed fluid outlet rose. Engine frequency also increased with operating time to approximately a range between 112 and 123 Hz as predicted by the model. Compressed fluid power was calculated to be approximately 5 W.
In the fourth example, the complex and unrestrained motion of a free-piston, glow-plug configuration was measured as piston speed versus piston position as shown in FIG. 22. As a comparison, the free-piston model data and experimental data were compared to a model crank engine as shown in FIG. 23. The free-piston model accurately fits with the resulting experimental data indicating that the model was able to accurately predict engine dynamics.
The fifth experiment was conducted comparing a free-piston engine with a crankshaft engine of the same size also utilizing glow-plug ignition. Results, as shown in FIG. 24, indicate that a higher compression ratio of around 10 in the free-piston engine resulted in average cycle efficiency of approximately 18.1 percent as compared to the compression ratio of 5.3 and average cycle efficiency of about 22 percent of the crankshaft engine.
The sixth experiment was conducted to compare model HCCI performance with model glow-plug ignition performance and experimental glow plug performance. Results, as shown in FIG. 25, indicate that model glow-plug ignition performance accurately predicted the experimental glow-plug ignition performance. The model predicts that the heat release efficiency of the HCCI free-piston engine will be approximately 41 percent as compared to the 25 percent of the glow-plug engine.
A miniature fluid compression engine is illustrated within FIGS. 26 and 27. The cylinder was specifically constructed for test purposes and was made of stainless steel with cylinder liners made of chrome plated brass. The dimensions of this specific example of an engine of the present invention includes the device being approximately 110 millimeters in length and approximately 38 millimeters in diameter with a 12.5 millimeter inside bore. With an attached carburetor and muffler, the engine system was approximately 75 millimeters wide. The operating frequency of the engine was optimized by adjusting the weight of the piston assembly and the stiffness of the spring to avoid leakage (which may be caused by a low frequency), high friction and noise (which may be caused by a high frequency). The pistons were preferably made of aluminum alloy, resulting in a weight of the moving parts of 33 grams. The spring system was made of steel and had a 1500 N/m resistance, measured approximately 2.5 millimeters in height at rest and has a pre-load force of 19 N. The system utilized glow plug ignition, a manual starter and a methanol-based fuel mixture. Using these parameters, the desired operating frequency of 100 Hz was achieved. As constructed, the combustion cylinder chamber had a volume measuring 0.13 cubic centimeters with a compressor cylinder chamber volume of 2.0 cubic centimeters when the spring was fully extended. When the spring was compressed completely, the engine cylinder chamber volume measured 1.7 cubic centimeters with a compressor cylinder chamber volume of 0.36 cubic centimeters. Designed with a 2 mm over-stroke, the engine is able to account for variations in piston travel, resulting in weak and strong cycles. The piston travel is long enough to enable scavenging and of a length that would result in metal to metal collision without the use of a bumper. Therefore a rubber bumper was incorporated to absorb some of the shock of the manual ignition handle impacting the cylinder. The energy balance of the engine is shown schematically in FIG. 28.
It is important to note that the construction and arrangement of the elements of the inventions as described in this application and as shown in the figures above is illustrative only. Although some embodiments of the present inventions have been described in detail in this disclosure, those skilled in the art who review this disclosure will readily appreciate that many modifications are possible without materially departing from the novel teachings and advantages of the subject matter recited. Accordingly, all such modifications are intended to be included within the scope of the present inventions. Other substitutions, modifications, changes and omissions may be made in the design, operating conditions and arrangement of the preferred and other exemplary embodiments without departing from the spirit of the present inventions.
It is important to note that the system and method of the present inventions can comprise conventional technology (e.g., engine cylinders, pistons, valves, carburetors, mufflers, fuels, lubricants, etc.) or any other applicable technology (present or future) that has the capability to perform the functions and processes/operations indicated in the FIGURES. All such technology is considered to be within the scope of the present inventions.
Patent Application
20130333368
