JP2000234501A - Energy reserving cycle engine mounting apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To decrease of NOx and increase an output by injecting steam from a steam injection valve 6 for a short time and at a suitable time to a wall surface of a diameter contracted main combustion chamber as well as carrying out combustion by mixing fuel with air in the combustion chamber. SOLUTION: A pair of diameter enlarged pistons 21 are continuously connected to a crankshaft 16, and respective pistons 21 are fitted to a pair of cylinder heads 15 disposed opposing to each other. A fuel injection valve 7B and an ignition device 8 are disposed to be faced to a diameter contracted main combustion chamber 1 partitioned into each cylinder head 15, air injected from an air flow path 9 and fuel injected from a fuel injection valve 7 are agitated and mixed with each other, and ignition combustion is carried out. Steam is injected from an outer periphery of a steam injection valve 6 through a steam supplying-out valve 4 and a steam, reservoir 5 at a suitable time and for high speed and super short time, and a combustion chamber wall surface is cooled to decrease the rate of NOx and increase an output. A turbo supercharger 12 is operated by energy of exhaust delivered from a diameter enlarged combustion chamber 10, and a rotary type supercharger 14 is operated by an electric motor 17 or the like, and intake air is supercharged.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention utilizes the third law of conservation of mechanical energy in order to increase the energy conversion efficiency of a piston cycle, which converts the reciprocating motion of a piston into rotational power, and uses the third law of conservation of mechanical energy near the dead center. The amount of energy released (stroke volume of the piston) is very small, and most of the heat energy is increased by saving the isolated combustion in the reduced diameter main combustion chamber (combustion near constant volume), saving the same compression ratio as gasoline engine and comparable to diesel engine. The energy-saving cycle internal combustion engine of the earlier application, which enables the highest combustion pressure, for example, releases the isolated combustion in the reduced diameter main combustion chamber after 30 degrees of the crank angle after the dead center to enhance the energy conversion efficiency and greatly improve the combustion. The present invention relates to addition and improvement of a mechanism according to the use of an engine.

[0002]

2. Description of the Related Art As a conventional technique, there is a worst-case constant-capacity cycle engine and a constant-pressure cycle engine in basic theory, which are the prime of applied research without any basic research, and are used for driving various machines such as vehicles, ships, and agricultural machines. The gasoline engine has a very low thermal efficiency of 15% to 25%, and is used to increase heat efficiency by delaying combustion.
Diesel engines may endanger humanity, such as sperm count reduction due to unburned pollution.
There is an urgent need to reduce pollution. That is, since the combustion chamber of a constant volume cycle engine or a constant pressure cycle engine is formed between the inner surface of the cylinder head and the upper surface of the piston, the maximum combustion pressure and the maximum combustion temperature are applied to the large-diameter combustion chamber, and cooling is indispensable. In addition to increasing cooling loss due to the inability to use cooling heat, increasing the maximum combustion pressure greatly increases the weight per unit output and friction loss, making it difficult to increase the light weight, large output, and thermal efficiency. .

[0003] In the combustion, there is usually a combustion period of about 30 degrees before and after the dead center to 60 degrees after the dead center, and a technology for effectively utilizing this combustion period to the utmost is expected.
When the piston starts to recede from the dead center, combustion is performed with the combustion chamber communicating with the inside of the cylinder.The volume of the combustion chamber rapidly increases with the retraction of the piston, resulting in extremely non-constant volume combustion and the same compression. Combustion pressure and thermal efficiency in the ratio must be reduced. Further, in addition to the decrease in thermal efficiency, the combustion pressure and the combustion temperature rapidly decrease, and the combustion state suddenly shifts to the worst combustion condition. Combustion results in increased NOx, both of which result in the worst pollutant-enhanced combustion, with disadvantages of the prior art that are so difficult that there is little room for improvement.

[0004] In addition, the reciprocating internal combustion engine of the prior art delays the combustion to increase the thermal efficiency. Therefore, in addition to an increase in various types of pollution due to a significant shortage of the combustion time, the thermal efficiency further decreases due to the deterioration of the combustion. Therefore, to increase thermal efficiency,
Inevitably results in an ultra-high compression ratio and ultra-long stroke, with a thermal efficiency of 55%
In order to achieve this level, the weight per output becomes extremely large, making it unusable for applications that require light weight and large output, such as automobiles. Now, the line of black smoke squirting vehicles is in distress every day, and the ban on the production of diesel vehicles is urgent. In addition, a gasoline engine that has accelerated combustion has a thermal efficiency of 25% to 1%.
There is a disadvantage that it is greatly reduced to about 5%.

[0005]

There is an urgent need to reduce pollution, including reduction of CO2 and prevention of global warming. This invention places the highest priority on basic research and seeks to the maximum possible use of the laws of nature. As the energy conservation cycle, the reciprocating motion of the piston is converted into the rotational motion, the energy conversion efficiency of the piston cycle is enhanced, and the pollution reduction including the reduction of CO2 is greatly reduced. The purpose is to expand from large to ultra-small and to add and improve the mechanism according to the application.

[0006]

SUMMARY OF THE INVENTION In view of the above-mentioned problems, the present invention has been developed to replace the conventional constant-volume cycle engine and constant-pressure cycle engine, in which it is difficult to reduce pollution including reduction of CO2 due to lack of basic research. The adoption of a preservation cycle greatly reduces the non-rotational release heat energy loss, which is the heat energy loss that acts in the direction that prevents rotation, and greatly increases thermal efficiency. Furthermore, the adoption of full elastic collision reciprocating motion or full elastic collision opposing reciprocating motion greatly reduces the kinetic energy reduction loss, which is the loss of kinetic energy due to reciprocating motion, and greatly increases thermal efficiency. Furthermore, adopting an energy conservation cycle greatly improves combustion, greatly reduces pollution, and greatly increases thermal efficiency. Furthermore, by adopting full elastic collision reciprocating motion or full elastic collision opposing reciprocating motion and energy conservation cycle, it is possible to greatly reduce vibration and enable extremely small and lightweight large specific output, from ultra-large to ultra-small applications. We will add and improve applications and mechanisms to expand and use as internal combustion engines for driving, general purpose and power generation of ships, aircraft, vehicles, various wheels and various machines.

As shown in FIG. 1 and FIG. 11, in the energy saving cycle internal combustion engine, the two-stage combustion of the reduced-diameter main combustion chamber 1 and the expanded-diameter combustion chamber 10 is performed when the ignition timing is greatly advanced, the constant-volume large-close agitated combustion is performed, and when the isolation is released. High-speed agitated combustion, which greatly improves combustion, so the mainstream is fully elastic collision reciprocating motion as a two-cycle simple structure. In addition, constant-pressure large-aperture agitated combustion allows the rise in combustion pressure at the same compression ratio to be released until isolation. Continuously, the maximum combustion pressure also rises greatly, and the greatly increased velocity-type heat energy + volume-type heat energy is concentrated and injected at high speed to the expanding piston. You. By greatly improving the combustion, the ultra-short stroke ultra-high speed with the diameter-expanding piston 21 and the diameter-reducing piston 22 is made possible. D-type and E-type energy-storing cycle internal combustion engines are used for complete elastic collision opposing reciprocating motion, but are not limited to 2-cycle D-type and E-type energy-storing cycle internal combustion engines. To apply.

As shown in FIGS. 1 to 8, in the energy storage cycle internal combustion engine, the expanded combustion chamber 10 is an ultra-high-speed expanded combustion chamber having a significantly lower pressure than that of the prior art, and the expanded piston 21 is also greatly expanded. The mainstream is ultra-high-speed engines with ultra-short strokes, where the piston stroke is smaller than the piston diameter, and with the same piston diameter, higher rotation speed than the conventional technology. In a reduced-diameter main combustion chamber having a certain volume or more, steam is supplied to an optional heat exchanger 2 including an approximate once-through boiler and a reduced-diameter main combustion chamber 1 including a one-way air passage 9 disclosed in the earlier application. Delivery valve 4 and steam delivery solenoid valve 4
A and steam injection mushroom valve 6, steam injection electromagnetic mushroom valve 6A, fuel vapor injection electromagnetic valve 7, steam injection electromagnetic valve 7A, known fuel injection valve 7B, fuel injection electromagnetic valve 7C, steam water injection electromagnetic valve 7D, and water injection electromagnetic The valve 7E, the known ignition device 8 and the known preheating ignition device 8A are added and deleted as appropriate. New mechanisms such as control devices will be added as appropriate, including the configuration of the supercharging cycle including the turbocharger 12 and the rotary supercharger 14. For the reduced diameter main combustion chamber with a certain volume or less, the added applications, configurations and mechanisms will be reduced appropriately and new mechanisms will be added as appropriate.

[0009]

FIG. 1 to FIG. 8 show an embodiment of the present invention.
As shown in FIG. 1, the energy storage cycle internal combustion engine delays only the heat energy release time as an energy storage cycle, greatly reduces the non-rotational release heat energy loss of the conventional gasoline engine around 40%, and reduces the thermal efficiency. And greatly improve combustion. Furthermore, as a two-stroke double-headed piston, the right dead center and the left dead center are fully elastic collision reciprocating motions in the explosion process, and the kinetic energy reduction loss of the conventional gasoline engine around 30% approaches 0%. Furthermore, it can be very easily configured as a piston with a large diameter by directly driving the crankshaft as a piston. The large-diameter combustion chamber can be made lighter as the pressure becomes lower, and the piston stroke S
The smaller the ratio of S / D = 1/4 to the cylinder inner diameter D, the lighter and larger the output can be made, and the production cost per output can be greatly reduced. In the process of adding and reducing various mechanisms from ultra-large to ultra-small applications as an internal combustion engine that can simultaneously achieve the limits of manufacturing cost reduction and CO2 reduction and global warming prevention pollution reduction, explanations are also added sequentially Reinforce and avoid duplicate descriptions.

As described above, due to the great improvement in combustion, the energy saving cycle internal combustion engine shown in FIG. The isolated combustion can also be a constant-volume, large-close agitated combustion with advanced ignition timing compared to the conventional technology, so that the maximum combustion pressure at the same compression ratio can be greatly increased. Since the thermal energy is greatly increased by the gas injection, and the heat load of the expanded combustion chamber is greatly reduced and the engine becomes a light-weight, high-output high-speed engine, NO is used in the reduced-diameter main combustion chamber having a certain volume or more.
x Heat exchanger 2 and various steam injection devices will be installed as appropriate to increase x output. The heat exchanger 2 is preferably a heat exchanger 2 having one or more steam conducting pipes 3. A steam delivering valve 4 is provided at the end point of the steam conducting pipe 3, and the steam delivering valve 4 which can be opened to the steam reservoir 5 in a timely manner is provided. It is possible to select the optimal opening / closing control including the above. The steam injection mushroom valve 6 and the fuel injection valve 7B are provided in the reduced-diameter main combustion chamber 1 so that they can be opened in a timely manner, and the ignition device 8 is provided so that they can be fired in a timely manner.
Contact the energy storage cycle general controller 20 of
The air flow and fuel injected from the one-way air flow path 9 are mixed and combusted, and steam is injected as appropriate to reduce NOx to almost zero.

Referring to the first embodiment of the energy conservation cycle engine shown in FIG. 1, description will be given including the general control device 20 shown in FIG. A fuel injection valve 7B and an ignition device 8 for opening and closing and igniting the reduced-diameter main combustion chamber 1 of the first embodiment of the cylinder head 15
The fuel is injected and mixed with the fuel injected from the one-way air flow path 9 and the fuel injected from the fuel injection valve 7B, ignited and burned by the igniter 8, and the steam is supplied in a timely manner.
A predetermined amount of steam is injected through the steam reservoir 5 from the outer periphery of the steam injection mushroom valve 6 toward the wall surface of the reduced-diameter main combustion chamber 1 in a high-speed and ultra-short time, and directly with water or wet steam having a large specific gravity. The wall is cooled to convert the radiant heat into dry steam, reduce NOx and increase the output by dry steam and the like, and increase the diameter of the combustion chamber 1.
0 to the exhaust duct 11, the turbocharger 12 is operated by the exhaust energy, the supply pressure of the supply duct 13 is increased, and the rotary supercharger 14 is controlled to operate at a rotational speed. The pressure is further increased and established appropriately, and the expanded combustion chamber 10 is supplied with air. In the control operation of the rotary supercharger 14, the rotation of the rotary supercharger 1 is performed by using the rotation of the crankshaft 16 as the rotation of the input shaft 18 and the output shaft 19 of the starting motor / generator 17 during operation.
4, the power is appropriately generated and stored in the power storage device 28, and at the time of starting, the starting motor 17 is operated by the stored power of the power storage device 28, and the rotary supercharger 14 and the crankshaft 16 are rotated. Air is supplied to the expanded combustion chamber 10 to start the energy saving cycle internal combustion engine. Therefore, it is preferable that the input shaft 18 and the output shaft 19 can be changed in speed depending on the application.

A description will be given of a case where a second embodiment of the cylinder head 15A of FIG. 2 is used instead of the first embodiment of the cylinder head 15 of FIG. A steam delivery solenoid valve 4A is provided at the end of the steam guide pipe 3 of the heat exchanger 2 so as to open and close the steam reservoir 5 of the steam injection solenoid valve 6A.
To be able to ignite, steam injection electromagnetic mushroom valve 6A, fuel injection valve 7B
An ignition device 8 is provided, and the air injected from the one-way air flow path 9 and the fuel injected from the fuel injection valve 7B of the prior art are mixed and agitated and ignited by the known ignition device 8 to reduce the diameter of the main combustion. Room constant volume large close-separated combustion / steam injection solenoid mushroom valve 6
Injection of high-speed swirling steam from the outer periphery of the mushroom valve including the swirling blade 27 of A as / NOx reduction / output increase combustion, release the isolated combustion at the optimal maximum combustion pressure, and put the combustion gas + superheated steam on the top of the expanded piston 21. Intense super high-speed injection, impulse +
The most efficient conversion to rotational power by reaction is performed, and unburned components are eliminated by ultra-high-speed agitation combustion.The combustion gas is absorbed into as much steam as possible in the process of temperature change to reduce pollution and reduce combustion. Adds chemicals, such as chemicals, to the water in the combustion chamber to reduce the pollution to a large extent.
Exhaust gas is discharged to the exhaust duct 11 as a small amount of lower temperature combustion gas. Steam injection solenoid valve 6A and steam delivery solenoid valve 4A
The permanent magnet 25 is fixed to the valve stem 23 of each husband and the electromagnet 26 is fixed to the valve box 24 of each husband, and the magnet is formed by one or more electromagnets 26 and one or more permanent magnets 25. Configure the section to enable timely steam delivery and steam injection.

[0013] Instead of the cylinder head 15 of FIG.
The third embodiment of the cylinder head 15B will be described. A fuel vapor injection solenoid valve 7 is provided at the end point of the steam guide pipe 3 so that fuel and steam can be injected into the reduced diameter main combustion chamber 1 and ignited.
Is appropriately mixed with the air injected from the one-way air flow path 9 and the fuel injected from the fuel vapor injection solenoid valve 7, and the high-temperature compression ignition is performed by the preheat ignition device 8A. The maximum combustion pressure at the same compression ratio is increased only by delaying the heat energy release timing and greatly increased by the fuel vapor injection solenoid valve 7 at the optimum time by the constant-volume close-separated combustion in the reduced-diameter main combustion chamber. As injection, NOx reduction, and output increase combustion, the isolated combustion is released at the optimum maximum combustion pressure, and the combustion gas + heated steam is intensively injected at the top of the expanded piston 21 at an ultra-high speed, and the most efficient by the impulse + reaction In addition to converting to rotational power, ultra-high-speed agitation combustion eliminates all unburned components, and in the process of temperature change, the combustion gas is absorbed into as much water vapor as possible, resulting in combustion with greatly reduced pollution. As chemicals added pollution large reduction and output a large increase combustion such, and exhausted to the exhaust duct 11 side of the enlarged diameter combustion chamber 10 as a low-temperature small quantity of the combustion gas.
The magnet part of the fuel vapor injection solenoid valve 7 has a valve stem 23.2
3A, a permanent magnet 25 is fixed to each of the valve boxes 24, and an electromagnet 26 is fixed to each of the valve boxes 24. A magnet unit is constituted by at least one of the electromagnets 26 and at least one of the permanent magnets 25. Make injection possible.

Instead of the cylinder head 15 of FIG. 1, FIG.
The case where the fourth embodiment of the cylinder head 15C is used will be described. A steam injection solenoid valve 7A is provided at the end point of the steam guide pipe 3 so that fuel and steam can be injected into the reduced diameter main combustion chamber 1 and ignited.
A fuel injection electromagnetic valve 7C and an ignition device 8 are provided as appropriate, and the air injected from the one-way air flow path 9 and the fuel injected from the fuel injection electromagnetic valve 7C are agitated and mixed to form a known ignition device 8C. And the maximum combustion pressure at the same compression ratio is delayed only by the heat energy release timing and greatly increased compared with the prior art by delaying only the heat energy release timing. More steam injection, NOx reduction,
When the output is increased, the exhaust is discharged from the expanded combustion chamber 10 to the exhaust duct 11 side when the combustion is separated and the combustion is released. The magnet parts of the steam injection solenoid valve 7A and the fuel injection solenoid valve 7C are configured such that a permanent magnet 25 is fixed to each of the valve rods 23, and an electromagnet 26 is fixed to each of the valve boxes 24. The above electromagnet 26 and one or more permanent magnets 2
5 constitutes a magnet part, which enables timely fuel injection and steam injection.

Instead of the cylinder head 15 of FIG. 1, FIG.
A description will be given of a case where the fifth embodiment of the cylinder head 15D is used. A steam injection solenoid valve 7A is provided at the end point of the steam guide pipe 3 so that fuel and steam can be injected into the reduced diameter main combustion chamber 1 and ignited.
A known fuel injection valve 7B and an igniter 8 or a preheating igniter 8A are provided as appropriate, and the air injected from the one-way air flow path 9, the fuel injected from the fuel injection valve 7B, and the type of the fuel are determined. Regardless of gasoline, light oil, heavy oil, propane, hydrogen, natural gas, methanol, methane, or alcohol, the mixture is stirred and mixed, and the igniter 8 or the preheating igniter 8A
By the compression ignition, the maximum combustion pressure at the same compression ratio is greatly increased compared to the prior art by the constant-volume close-separated combustion in the reduced-diameter main combustion chamber, and the steam injection / NOx reduction from the steam injection solenoid valve 7A at the optimum time. The combustion is increased from the expanded combustion chamber 10 to the exhaust duct 11 side as the combustion with increased output, and the combustion is released at the optimal time as the combustion with isolated combustion released and the pollution is reduced.

A case will be described in which a sixth embodiment of the cylinder head 15E of FIG. 6 is used instead of the first embodiment of the cylinder head 15 of FIG. A fuel water injection solenoid valve 7D, an ignition device 8 and the like are provided to inject fuel into the reduced diameter main combustion chamber 1 to inject water so as to be ignitable and reduce NOx, and air injected from the one-way air flow path 9 And the fuel injected from the fuel water injection solenoid valve 7D are stirred and mixed, ignited by a known ignition device 8, and the maximum combustion pressure at the same compression ratio is reduced by the constant-diameter main combustion chamber constant volume large close-separation combustion. Great rise from the conventional technology,
The high pressure water in the water reservoir 5A is discharged to the exhaust duct 11 from the expanded combustion chamber 10 at the optimal time as water injection and NOx reduction combustion from the fuel water injection solenoid valve 7D and at the optimal time as the isolated combustion release pollution reduction output increase combustion. . The magnet portion of the fuel water injection solenoid valve 7D is provided with permanent magnets 25
The magnet part is fixed to the valve box 24, and the magnet part is composed of one or more electromagnets 26 and two or more permanent magnets 25 so that fuel injection and water injection can be performed at appropriate times.

A case will be described in which the seventh embodiment of the cylinder head 15F of FIG. 7 is used instead of the first embodiment of the cylinder head 15 of FIG. A water injection solenoid valve 7E, a fuel injection valve 7B, and an ignition device 8 are provided so that fuel and water can be injected into the reduced diameter main combustion chamber 1 and ignited. Agitated and mixed with the fuel injected from the valve 7B, ignited by the known ignition device 8, and the maximum combustion pressure at the same compression ratio is greatly increased by the known small-diameter main combustion chamber at the same compression ratio as compared with the prior art. Then, the water is discharged from the large-diameter combustion chamber 10 toward the exhaust duct 11 as water injection and NOx reduction combustion from the water injection solenoid valve 7E at the optimum time, and as isolated combustion release pollution reduction output increase combustion at the optimum time. The magnet part of the water injection solenoid valve 7E has the permanent magnets 25 fixed to the valve rod 23 and the electromagnet 26 fixed to the intermediate valve box 24,
The magnet part is composed of one or more electromagnets 26 and two or more permanent magnets 25 so that water can be jetted at appropriate times.

Referring to FIG. 8, the control device will be described with reference to FIGS. As a united control device, various control devices are built in the energy storage cycle general control device 20, and a sensing unit, a calculation unit, a regulation unit, etc. are provided to detect and calculate the temperature, pressure, rotation speed, etc. of each unit.・ Restrict pollution and reduce pollution, including optimal combustion control, etc., and greatly increase thermal efficiency. That is, the fuel injection compression ignition combustion from the fuel vapor injection solenoid valve 7 or the fuel injection valve 7B or the fuel injection solenoid valve 7C and the igniter 8 or the preheating igniter 8A is controlled by the optimal fuel injection ignition control and the optimal combustion by the detection calculation regulation or the like. As control, high-speed steam injection from the fuel steam injection solenoid valve 7 or the steam injection solenoid valve 7A or the steam injection solenoid valve 6A or the steam injection mushroom valve 6 is performed as an optimum steam injection control according to detection calculation regulation or the like.
Ox is reduced to make almost no NOx combustion, and steam energy injection is used to increase the additional power to achieve constant-volume, close-separation combustion, which reduces pollution and greatly increases thermal efficiency. Also, in a small and inexpensive energy storage cycle internal combustion engine without the heat exchanger 2, water injection is used instead of steam injection, and the water injection solenoid valve 7D
High-speed water injection from the plant is optimized for water injection control based on detection calculation regulations, etc., and reduction in pollution and increase in thermal efficiency are achieved with large-diameter isolated combustion in the reduced-diameter main combustion chamber 1.

That is, the maximum combustion pressure and the maximum combustion temperature are continuously increased by the constant-volume close-separation combustion in the reduced-diameter main combustion chamber 1, and the maximum combustion pressure and the maximum combustion temperature at the same compression ratio are greatly increased as compared with the prior art. Then, the greatly increased thermal energy is concentrated and injected at high speed to the top of the diameter-enlarged piston 21 by isolated combustion release combustion, thereby reducing ultra-high-speed pollution, completely eliminating combustion, and greatly increasing output re-combustion. The diameter expansion piston is moved strongly by the pressure heat energy, and the heat energy release is concentrated on the perfect rotary power conversion efficiency (90 degrees before dead center), and the concept of the conventional technology is reversed to reduce pollution and output. Increases thermal efficiency. The exhaust gas is operated by operating the turbocharger 12 of the exhaust duct 11 from the expanded combustion chamber 10 and the heat exchanger 2.
The air discharged to the side or directly to the atmosphere and sucked from the turbocharger 12 is boosted directly or by the rotary supercharger 14 through the air supply duct 13 and supplied to the expanded combustion chamber 10. You. Therefore, during operation, the rotary supercharger 14 is operated by the rotational force of the crankshaft 16, and at the start, the crankshaft 16 and the rotary supercharger 14 are rotated and started by the starting motor / generator 17. However, since various conditions change, such as the outside air temperature ゃ when stopped or when operating for a long time, the general control device 20 has a built-in rotation speed control device, and the temperature and rotation speed of each part and the power storage device 2
Detecting, calculating, and regulating the amount of stored electricity in 8 and controlling the optimal rotation speed of the starting motor / generator 17 and the input shaft 18 and output shaft 19, the control device is adapted to the starting time and various operating conditions.

Referring to the second embodiment of the energy storage cycle engine shown in FIG. 9, when used as various engines close to the limit of a small size such as a model airplane, the energy storage cycle engine has a reciprocating motion and a rotary motion. As a configuration that greatly reduces the kinetic energy reduction loss, in which the motion direction is suddenly reversed and consumes kinetic energy, a configuration in which a full elastic collision reciprocating motion and a configuration in which all motion portions rotate in the same direction are adopted as the core. The kinetic energy reduction loss of the conventional gasoline engine has been reduced from around 30% to 0%. In addition, as a configuration that greatly reduces non-rotational release heat energy loss, which is a loss that increases rotation inhibiting force, such as an increase in friction loss and a force acting in the reverse rotation direction, a conventional gasoline using an energy storage cycle system Engine non-rotating release heat energy loss 40
% Has been greatly reduced. Accordingly, although a patent application has been filed mainly for an example of adopting the energy conservation cycle system, an example of adopting only a configuration that greatly reduces the loss of kinetic energy will be described for a case where the engine is used as a micro model airplane engine. In other words, when it is difficult to adopt the energy conservation cycle method such as a small-sized model airplane engine, it is assumed that only full elastic collision reciprocation is adopted, and as shown in FIG. The point should also be a full elastic collision reciprocating motion with an explosion stroke, and the supercharger is only a rotary supercharger 14,
Attaching to the engine main body air supply duct 13 so as to be operable is good for reducing kinetic energy loss and reducing combustion loss.

The third of the energy conservation cycle engines of FIG.
With reference to an embodiment, a case where the engine is used as a D-type energy storage cycle engine for various uses close to a small size such as for a brush cutter will be described. As described above, the energy storage cycle engine employs, as a configuration for greatly reducing the kinetic energy reduction loss, a configuration in which a complete elastic collision reciprocating motion and a configuration in which all the moving parts rotate in the same direction are used. As a configuration that greatly reduces the rotational heat energy loss, we have adopted the optimization of the isolated combustion release timing of the isolated combustion in the reduced diameter main combustion chamber as an energy conservation cycle. That is, in the case of a combined use of an energy storage cycle system, a fully elastic collision reciprocating motion system, and a system in which all the moving parts perform the same direction rotational motion, such as a D-type energy storage cycle engine for a brush cutter,
As shown in FIG. 10, a two-stroke double-headed piston adopting optimization of the isolated combustion release timing of the reduced diameter main combustion chamber has a completely elastic collision reciprocating motion in which both the right dead center and the left dead center have an explosion stroke. It is good to reduce the loss of kinetic energy and to reduce the loss of the kinetic energy, and the fuel injection timing in the reduced-diameter main combustion chamber 1 is determined at the end point of the intake stroke by using only the rotary supercharger 14 and operably attached to the engine main body air supply duct 13. From the end of the suction stroke to the end of the suction stroke, when the low pressure gas, such as propane gas, is selected as appropriate according to the fuel injection pressure until the end of the compression stroke. Early injection,
Injection is terminated so that it accumulates in the reduced-diameter main combustion chamber 1, and other technologies are used as needed for the rest.

Referring to FIG. 1 and FIG. 10, D for various uses close to small, such as for small boats, outboard motors, and general-purpose engines,
The case of using as a type energy conservation cycle engine will be described. The energy conservation cycle engine employs a configuration that reciprocates completely elastically and a configuration in which all the moving parts rotate in the same direction to greatly reduce the loss of kinetic energy. In order to greatly reduce the loss of non-rotating heat energy, the energy saving cycle has been adopted to optimize the isolated combustion release timing of the reduced-diameter main combustion chamber isolated combustion. That is, in the case of using the energy storage cycle system such as the D-type energy storage cycle engine for an outboard motor, the fully elastic collision reciprocating motion system, and the system in which all the moving parts rotate in the same direction, FIG. As described above, a two-stroke double-headed piston adopting optimization of the isolated combustion release timing of the reduced diameter main combustion chamber has a completely elastic collision reciprocating motion in which the right dead center and the left dead center have an explosion stroke, and the engine body is operable. As the supercharger in the air supply duct 13, only the rotary supercharger 14 or a combination with the turbocharger 12 is used.
Attaching the turbocharger 12 to the exhaust duct 11
The fuel injection timing in the reduced-diameter main combustion chamber 1 is appropriately selected in accordance with the fuel injection pressure from the end point of the suction stroke to the end point of the compression stroke. When injecting pressure gas such as gas into the fuel injection valve as it is, low-pressure early injection is performed in the compression stroke from the end point of the suction stroke, and the injection is stopped so as to accumulate in the reduced diameter main combustion chamber 1. For other fuel injection timings, the conventional in-cylinder fuel injection combustion is changed from time to time to the reduced diameter main combustion chamber fuel injection combustion, and the injection combustion timing is used as appropriate and used, including various solenoid valves. The reduced-diameter main combustion chamber with a certain volume or more will be replaced by the steam-internal combustion engine combustion chamber as shown in Fig. 1.

Referring to FIG. 1 and FIG. 11, when used as D-type and E-type energy storage cycle engines for various near-medium-sized applications such as automobiles and marine vessels, the energy storage cycle Full elastic collision reciprocating motion system, full elastic collision opposing reciprocating motion system, and a system in which all moving parts rotate in the same direction as a configuration that greatly reduces the reduction loss and a configuration that greatly reduces the non-rotational release heat energy loss And energy conservation cycle system. That is, in the case of a conventional D or E type energy storage cycle engine for automobiles or marine vessels, a combination of an energy storage cycle system, a fully elastic collision reciprocating motion system, and a system in which all moving parts rotate in the same direction is used. 1. As shown in Fig. 11, a two-stroke double-headed piston is used as a D-type energy conservation cycle engine with a right dead center and a left dead center that have an explosion stroke, or an E-type energy conservation cycle engine that has a D-type opposed to it to greatly reduce vibration. . In addition to the full elastic collision reciprocating motion or the full elastic collision opposing reciprocating motion, the supercharger is operably provided in the engine main body air supply duct 13 in combination with the rotary supercharger 14 and the turbocharger 12. You. The installation of the turbocharger 12 in the exhaust duct 11 is good for reducing the kinetic energy reduction loss and increasing the thermal efficiency. The fuel injection timing in the reduced diameter main combustion chamber 1 is appropriately adjusted according to the fuel injection pressure in the latter half of the compression stroke. For the selected main combustion chamber with a smaller diameter than a certain volume, select the combustion chamber of the steam internal combustion engine shown in Fig. 1 as needed.

Referring to FIG. 1 and FIG. 11, for various applications such as power generation for large and near-medium sized vehicles such as those for conventional medium-sized and large marine vessels,
When used as a D-type or E-type energy storage cycle engine, the energy storage cycle engine is configured to completely reduce the kinetic energy reduction loss and to reduce the non-rotationally released heat energy loss to a completely elastic collision reciprocating motion. It adopts the method of reciprocating motion with complete elastic collision, the method of rotating all moving parts in the same direction, and the energy conservation cycle method. That is, conventional medium-sized
In the case of the D-type and E-type energy storage cycle engines for various applications such as large ships, such as the energy storage cycle system, the fully elastic collision reciprocating motion system, and the system in which all motion parts rotate in the same direction, As shown in FIGS. 1 and 11, an E-type energy conservation cycle engine in which a D-type or a D-type is provided as a two-cycle double-headed piston having both a right dead center and a left dead center in an explosion stroke, or a D-type is provided oppositely to greatly reduce vibration. will do. In addition to the full elastic collision reciprocating motion or the full elastic collision opposing reciprocating motion, the supercharger is operably provided in the engine main body air supply duct 13 in combination with the rotary supercharger 14 and the turbocharger 12. You. The turbocharger 12 is attached to the exhaust duct 11 to improve the kinetic energy reduction loss and increase the thermal efficiency. The fuel injection timing in the reduced diameter main combustion chamber 1 is reduced to the fuel injection pressure until the end of the compression stroke. Select according to your needs. The reduced-diameter main combustion chamber with a certain volume or more shall be the steam-internal combustion combined engine combustion chamber shown in Fig. 1.

With reference to FIGS. 12 and 13, an exchange-type reduced-diameter piston used in D-type and E-type energy conservation cycle engines will be described. The A-type exchange-type reduced-diameter piston (22AA) is a type that tightens the reduced-diameter piston from the enlarged-diameter piston 21 side regardless of the constituent material. The B-type interchangeable diameter-reducing piston (22BA) is a type that tightens the diameter-reduced piston with the enlarged diameter part from the diameter-reduced piston side regardless of the constituent material. The A-type coated exchange-type reduced diameter piston (22AB) is made by coating the surface of the constituent material with ceramics etc. to improve heat resistance. It is a reduced diameter piston that is tightened from the reduced diameter piston side. The B-type coated exchange-type reduced-diameter piston (22BB) is a type in which the surface of the constituent material is coated with a ceramic or the like to improve heat resistance, and is provided with an enlarged-diameter portion and tightened from the reduced-diameter piston side. The A-type ceramic exchange type reduced-diameter piston (22AC) is a reduced-diameter piston reinforced with ceramics as a constituent material and an expanded-diameter piston 21.
Tighten from the side. The B-type ceramic exchange type reduced-diameter piston (22BC) is a type in which a reduced-diameter piston reinforced with ceramics as a constituent material is provided with an enlarged-diameter section and tightened from the reduced-diameter piston side.

Referring to FIG. 14, a device mounted on an energy storage cycle engine having a device driven by rotational force will be described. The main devices driven by rotational force are energy conservation cycle engines such as various ships, various aircraft, various vehicles, various wheels, various machines, general-purpose internal combustion engines, internal combustion engines for power generation, and internal combustion engines for combined heat and electricity. All that can be driven by The driving method of the device driven by the rotational force includes all the methods that were driven by the conventional reciprocating internal combustion engine, and the power transmission device is provided as in the conventional technology. The controller uses an energy conservation cycle general controller 20 to use an energy conservation cycle engine instead of the conventional reciprocating internal combustion engine.

[0027]

According to the present invention, since the above-mentioned applications and configurations are added, the following effects can be obtained. 1. Since the diameter-reduced piston is easily replaced, the maintenance of the core part of the energy saving cycle engine is facilitated. 2. Easy replacement of the reduced-diameter piston and easy maintenance of the core of the energy conservation cycle engine, so that gasoline, light oil, heavy oil, propane gas, hydrogen, natural gas, methanol,
To decompress and leak combustion gas such as methane in multiple stages,
Fluctuation in the amount of leakage due to wear of the leakage part is eliminated, and control is facilitated. 3. The most important losses of the energy conservation cycle engine are the non-rotational heat energy loss and the kinetic energy reduction loss. Since it has been clarified that all the moving parts adopt the configuration of rotating in the same direction, it is easy to exchange the diameter-reduced piston for each application, thereby facilitating research and development.

[Brief description of the drawings]

FIG. 1 is a schematic partial sectional view showing a first embodiment of an energy storage cycle engine according to the invention.

FIG. 2 is a partial schematic sectional view showing a second embodiment as a cylinder head 15A.

FIG. 3 is a partial schematic sectional view showing a third embodiment as a cylinder head 15B.

FIG. 4 is a partial schematic sectional view showing a fourth embodiment as a cylinder head 15C.

FIG. 5 is a partial schematic sectional view showing a fifth embodiment as a cylinder head 15D.

FIG. 6 is a partial schematic sectional view showing a sixth embodiment as a cylinder head 15E.

FIG. 7 is a partial schematic sectional view showing a seventh embodiment as a cylinder head 15F.

FIG. 8 is an overall schematic diagram illustrating a general control system for various energy storage cycles according to the invention.

FIG. 9 is a schematic partial cross-sectional view showing a second embodiment of the energy storage cycle engine of the invention.

FIG. 10 is a schematic partial cross-sectional view showing a third embodiment of the energy storage cycle engine of the previous invention.

FIG. 11 is a schematic partial cross-sectional view showing a fourth embodiment of the energy storage cycle engine of the previous invention.

FIG. 12 is a partial sectional view showing a first embodiment of the core part of the energy conservation cycle engine of the present invention.

FIG. 13 is a partial sectional view showing a second embodiment of the core part of the energy conservation cycle engine of the present invention.

FIG. 14 is an overall configuration diagram showing an embodiment of an energy storage cycle engine mounted device of the present invention.

[Explanation of symbols]

1, a reduced diameter main combustion chamber, 2, a heat exchanger, 3, a steam pipe, 4, a steam delivery valve, 4A, a steam delivery solenoid valve, 5,
Steam reservoir, 5A, water reservoir, 6, steam injection mushroom valve, 6A, steam injection solenoid mushroom valve, 7, fuel vapor injection solenoid valve, 7A,
7B, fuel injection solenoid valve, 7C, fuel injection solenoid valve, 7D, fuel water injection solenoid valve, 7E, water injection solenoid valve, 8, ignition device, 8A, preheating ignition device,
9, one-way air flow passage, 10, expanded combustion chamber, 11, exhaust duct, 12, turbocharger, 13, air supply duct, 14, rotary supercharger, 15, cylinder head,
16, crankshaft 17, starting motor and generator,
18, input shaft, 19, output shaft, 20, energy storage cycle general control device, 21, expanding piston, 2
2, reduced diameter piston, 22AA, A type exchangeable diameter reduction piston, 22BA, B type exchangeable diameter reduction piston, 22A
B, A type exchangeable reduced diameter piston, 22BB, B type exchangeable reduced diameter piston, 22AC, A type exchangeable diameter reduced piston, 22BC, B type exchangeable diameter reduced piston, 23, valve stem, 23A , Valve stem,
24, valve box, 25, permanent magnet, 26, electromagnet, 2
7, turning blade, 28, power storage device, 29, engine body,

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F02M 25/032 F02M 25/02 C 25 / 022H

Claims (145)

[Claims] 1. A heat exchanger (2) for supplying steam to a reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection mushroom valve (6) provided with a swirl vane (27) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1), and a fuel injection valve opening to the reduced diameter main combustion chamber (1) (7B) An energy storage cycle engine-equipped device having an ignition device (8), a one-way air flow path (9), and a device driven by rotational force. 2. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), an A-type exchange-type reduced-diameter piston (22AA), and a device driven by a rotational force. 3. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), an A-type exchangeable reduced-diameter piston (22AB), and a device driven by a rotational force. 4. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), an A-type ceramic exchange type reduced-diameter piston (22AC), and a device mounted on an energy storage cycle engine that is driven by a rotational force. 5. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), a B-type exchange-type reduced-diameter piston (22BA), and a device driven by a rotational force. 6. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), a B-type cover exchange type reduced-diameter piston (22BB), and a device driven by a rotational force. 7. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery valve (4) and a steam reservoir (5) provided in the steam guide pipe (3), A steam injection valve (6) opening from the steam reservoir (5) to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1); and an ignition device (8) ), A one-way air flow path (9), a B-type ceramic exchange type reduced diameter piston (22BC), and a device mounted on an energy storage cycle engine, which is driven by a rotational force. 8. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam pipe (3), and a steam reservoir (5). Steam injection mushroom valve (6) provided with swirl vanes (27) opening to the reduced diameter main combustion chamber (1)
And a fuel injection valve (7) opening to the reduced-diameter main combustion chamber (1).
B) and an ignition device (8), a one-way air flow path (9),
A device mounted on an energy storage cycle engine having a device driven by rotational force. 9. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow Road (9) and A-type interchangeable diameter reducing piston (22
AA) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 10. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow An energy storage cycle engine-equipped device having a path (9), an A-type coated exchange-type reduced-diameter piston (22AB), and a device driven by rotational force. 11. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a heat reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow A device mounted on an energy storage cycle engine having a path (9), an A-type ceramic exchange type reduced-diameter piston (22AC), and a device driven by rotational force. 12. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow Road (9) and B-type interchangeable diameter reducing piston (22
BA), and a device mounted on an energy storage cycle engine having a device driven by rotational force. 13. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow An energy storage cycle engine-equipped device having a road (9), a B-type coated exchange-type reduced-diameter piston (22BB), and a device driven by rotational force. 14. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection mushroom valve (6) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and a one-way air flow An energy storage cycle engine-equipped device having a path (9), a B-type ceramic exchange type reduced-diameter piston (22BC), and a device driven by rotational force. 15. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection mushroom valve (6) provided with a swirl vane (27) that opens to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) opened to the reduced diameter main combustion chamber (1), and an ignition device (8) An energy storage cycle engine-equipped device having a one-way air flow path (9) and a device driven by rotational force. 16. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); An energy storage cycle engine mounted device having an air flow path (9), an A-type exchange-type reduced-diameter piston (22AA), and a device driven by rotational force. 17. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); Air flow path (9) and A-type coated exchange-type reduced-diameter piston (22AB)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 18. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); The air flow path (9) and the A-type ceramic exchange type reduced diameter piston (22
AC) and a device driven by an energy storage cycle engine having a device driven by rotational force. 19. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); An energy storage cycle engine-mounted device having an air flow path (9), a B-type exchange-type reduced-diameter piston (22BA), and a device driven by rotational force. 20. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); Air flow path (9) and B-type coating exchange type reduced diameter piston (22BB)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 21. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
A steam injection electromagnetic mushroom valve (6A) opening to the reduced diameter main combustion chamber (1); a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1); An air flow path (9) and a B-type ceramic exchange type reduced diameter piston (22
BC) and a device that is driven by a rotational force and is mounted on an energy storage cycle engine. 22. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine mounted device having a flow path (9) and a device driven by rotational force. 23. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine mounted device having a flow path (9), an A-type exchange-type reduced-diameter piston (22AA), and a device driven by rotational force. 24. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine-equipped device having a flow path (9), an A-type coated exchange-type reduced-diameter piston (22AB), and a device driven by rotational force. 25. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine mounted device having a flow path (9), an A-type ceramic exchange type reduced diameter piston (22AC), and a device driven by a rotational force. 26. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine mounted device having a flow path (9), a B-type exchange-type reduced-diameter piston (22BA), and a device driven by rotational force. 27. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine-equipped device having a flow path (9), a B-type coated exchange-type reduced-diameter piston (22BB), and a device driven by rotational force. 28. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) and an ignition device (8) opening to the reduced diameter main combustion chamber (1), and one-way air An energy storage cycle engine mounted device having a flow path (9), a B-type ceramic exchange type reduced diameter piston (22BC), and a device driven by rotational force. 29. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an ignition device (8), a one-way air flow path (9), and a device driven by a rotational force. 30. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), an A-type exchange-type reduced-diameter piston (22AA), and a device driven by a rotational force. 31. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), an A-type cover exchange-type reduced-diameter piston (22AB), and a device driven by a rotational force. 32. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), an A-type ceramic exchange type reduced-diameter piston (22AC), and a device driven by a rotational force. 33. A heat exchanger (2) for supplying steam to the reduced diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), an exchangeable B-type reduced-diameter piston (22BA), and a device driven by a rotational force. 34. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), an exchange-type B-type reduced diameter piston (22BB), and a device driven by a rotational force. 35. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam delivery solenoid valve (4A) and a steam reservoir (5) provided in the steam guide pipe (3). , The steam reservoir (5)
, A steam injection electromagnetic mushroom valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). ) And an ignition device (8), a one-way air flow path (9), a B-type ceramic exchange type reduced-diameter piston (22BC), and a device driven by a rotational force. 36. A heat exchanger (2) for supplying steam to a reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an energy storage cycle engine device having an ignition device (8), a one-way air flow path (9), and a device driven by rotational force. 37. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an ignition device (8), a one-way air flow path (9), and an A-type exchange-type reduced-diameter piston (22AA)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 38. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an ignition device (8), a one-way air flow path (9), and an A-type covered exchange-type reduced-diameter piston (22A).
B) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 39. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an energy storage cycle engine equipped with an ignition device (8), a one-way air flow path (9), an A-type ceramic exchange type reduced-diameter piston (22AC), and a device driven by rotational force. 40. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an ignition device (8), a one-way air flow path (9), and a B-type exchange-type reduced diameter piston (22BA)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 41. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam guide pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And a igniter (8), a one-way air flow path (9), and a B-type cover exchange type reduced diameter piston (22B
B) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 42. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), a steam reservoir (5) provided in the steam-conducting pipe (3), and a steam reservoir (5). A steam injection solenoid valve (6A) and a swirl vane (27) opening to the reduced diameter main combustion chamber (1) so as to enable high-speed swirl injection, and a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1). And an energy storage cycle engine equipped with an ignition device (8), a one-way air flow path (9), a B-type ceramic exchange type reduced-diameter piston (22BC), and a device driven by rotational force. 43. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the steam-conducting pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). Energy having a fuel / steam injection solenoid valve (7), an ignition device (8) operating on the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and a device driven by rotational force. Equipment installed in a preservation cycle engine. 44. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the steam-conducting pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). Solenoid valve for fuel / steam injection (7), ignition device (8) operating on the reduced-diameter main combustion chamber (1), one-way air flow path (9), A-type exchange-type reduced-diameter piston (22AA) And an energy storage cycle engine-equipped device having a device driven by a rotational force. 45. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the heat-conducting steam pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). A fuel / steam injection solenoid valve (7), an igniter (8) operating on the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and an A-type cover exchange type reduced-diameter piston (22AB) ) And a device driven by a rotational force. 46. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the heat-conducting steam pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). A fuel / steam injection solenoid valve (7), an ignition device (8) operating on the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and an A-type ceramic exchange type reduced-diameter piston (22AC) ) And a device driven by a rotational force. 47. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the heat-conducting steam pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). Fuel / steam injection solenoid valve (7), ignition device (8) operating on the reduced-diameter main combustion chamber (1), one-way air flow path (9), B-type exchange-type reduced-diameter piston (22BA) And an energy storage cycle engine-equipped device having a device driven by a rotational force. 48. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the heat-conducting steam pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). A fuel / steam injection solenoid valve (7), an igniter (8) operating on the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and a B-type cover exchange type reduced-diameter piston (22BB) ) And a device driven by a rotational force. 49. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and the steam-conducting pipe (3) is provided so as to be openable in the reduced-diameter main combustion chamber (1). A fuel / steam injection solenoid valve (7), an ignition device (8) operating on the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and a B-type ceramic exchange type reduced-diameter piston (22BC) ) And a device driven by a rotational force. 50. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
A device mounted on an energy storage cycle engine having a device driven by rotational force. 51. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
An energy-saving cycle engine mounted device having an A-type exchange-type reduced-diameter piston (22AA) and a device driven by rotational force. 52. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
An energy storage cycle engine-mounted device having an A-type coated exchange-type reduced-diameter piston (22AB) and a device driven by rotational force. 53. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
A type ceramic exchange type reduced diameter piston (22AC),
A device mounted on an energy storage cycle engine having a device driven by rotational force. 54. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
An energy storage cycle engine-mounted device having a B-type exchange-type reduced-diameter piston (22BA) and a device driven by rotational force. 55. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
An energy-saving cycle engine-mounted device having a B-type coated exchange-type reduced-diameter piston (22BB) and a device driven by rotational force. 56. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable in the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
The fuel injection solenoid valve (7) opening to the reduced diameter main combustion chamber (1)
C) and an ignition device (8), a one-way air flow path (9),
B type ceramic exchange type reduced diameter piston (22BC),
A device mounted on an energy storage cycle engine having a device driven by rotational force. 57. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable in the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7) that opens to the reduced diameter main combustion chamber (1)
B) and an ignition device (8), a one-way air flow path (9),
A device mounted on an energy storage cycle engine having a device driven by rotational force. 58. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) that open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), an A-type exchange-type reduced diameter piston (22AA), and a rotational force And a device driven by the energy storage cycle engine. 59. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable in the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) that open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), an A-type covered exchange type reduced-diameter piston (22AB), and rotation An energy storage cycle engine mounted device having a device driven by force. 60. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam guide pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) which open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), an A-type ceramic exchange type reduced diameter piston (22AC), and rotation An energy storage cycle engine mounted device having a device driven by force. 61. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) opening to the reduced-diameter main combustion chamber (1), a one-way air flow path (9), a B-type exchange-type reduced-diameter piston (22BA), and a rotational force And a device driven by the energy storage cycle engine. 62. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable in the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) which open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), a B-type coated exchange-type reduced diameter piston (22BB), and rotation An energy storage cycle engine mounted device having a device driven by force. 63. A heat exchanger (2) for supplying steam to the reduced-diameter main combustion chamber (1), and steam injection provided in the steam-conducting pipe (3) so as to be openable to the reduced-diameter main combustion chamber (1). A solenoid valve (7A),
A fuel injection valve (7B) and an igniter (8) that open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), a B-type ceramic exchange type reduced diameter piston (22BC), and rotation An energy storage cycle engine mounted device having a device driven by force. 64. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an ignition device (8), a one-way air flow path (9), and a device driven by a rotational force. An energy storage cycle engine mounted device having: 65. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an igniter (8), a one-way air flow path (9), and an A-type exchange type reduced diameter. Piston (22AA)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 66. A fuel-water-injection solenoid valve (7D) capable of opening to the reduced-diameter main combustion chamber (1), an ignition device (8), a one-way air flow path (9), and an A-type cover exchange type contraction type. Diameter piston (22A
B) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 67. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an igniter (8), a one-way air flow path (9), and an A-type ceramic exchange type reduction. An energy storage cycle engine mounted device having a radial piston (22AC) and a device driven by rotational force. 68. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an igniter (8), a one-way air flow path (9), and a B-type exchange type reduced diameter. Piston (22BA)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 69. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an ignition device (8), a one-way air flow path (9), and a B-type cover exchange type contraction type. Diameter piston (22B
B) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 70. A fuel water injection solenoid valve (7D) capable of opening to the reduced diameter main combustion chamber (1), an igniter (8), a one-way air flow path (9), and a B-type ceramic exchange type reduction. An energy storage cycle engine mounted device having a radial piston (22BC) and a device driven by rotational force. 71. A water injection solenoid valve (7E) capable of opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1) and an ignition device (8). ), A one-way air flow path (9), and a device driven by a rotational force. 72. A water injection solenoid valve (7E) that can be opened to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) that opens to the reduced diameter main combustion chamber (1), and an ignition device (8). ), A one-way air flow path (9), and an A-type exchange-type reduced-diameter piston (22A).
A) An energy storage cycle engine-equipped device comprising: A) and a device driven by a rotational force. 73. A water injection solenoid valve (7E) capable of opening to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) opening to the reduced diameter main combustion chamber (1) and an ignition device (8). ), A one-way air flow path (9), and an A-type covered exchange-type reduced-diameter piston (22).
AB) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 74. A water injection solenoid valve (7E) that can be opened to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) that opens to the reduced diameter main combustion chamber (1), and an ignition device (8). ), A one-way air flow path (9), an A-type ceramic exchange type reduced-diameter piston (22AC), and a device mounted on an energy storage cycle engine that is driven by a rotational force. 75. A water injection solenoid valve (7E) that can be opened to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) that opens to the reduced diameter main combustion chamber (1), and an ignition device (8). ), A one-way air flow path (9), and a B-type exchange-type reduced-diameter piston (22B).
A) An energy storage cycle engine-equipped device comprising: A) and a device driven by a rotational force. 76. A water injection solenoid valve (7E) that can be opened to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) that opens to the reduced diameter main combustion chamber (1), and an ignition device (8). ), A one-way air flow path (9), and a B-type cover exchange type reduced diameter piston (22).
BB) and a device mounted on an energy storage cycle engine having a device driven by rotational force. 77. A water injection solenoid valve (7E) that can be opened to the reduced diameter main combustion chamber (1), a fuel injection valve (7B) that opens to the reduced diameter main combustion chamber (1), and an ignition device (8). ), A one-way air flow path (9), a B-type ceramic exchange type reduced diameter piston (22BC), and a device mounted on an energy storage cycle engine, which is driven by a rotational force. 78. A fuel injection valve (7B) and an igniter (8) that open to the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and an A-type exchange-type reduced-diameter piston (22AA). )When,
A device mounted on an energy storage cycle engine having a device driven by rotational force. 79. A fuel injection valve (7B) and an igniter (8) that open to the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and an A-type cover exchange-type reduced-diameter piston ( 22AB)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 80. A fuel injection valve (7B) and an igniter (8) that open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), an A-type ceramic exchange type reduced diameter piston ( 2
2AC) and a device that is driven by a rotational force. 81. A fuel injection valve (7B) and an igniter (8) that open to the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and a B-type exchange-type reduced-diameter piston (22BA). )When,
A device mounted on an energy storage cycle engine having a device driven by rotational force. 82. A fuel injection valve (7B) and an igniter (8) that open to the reduced-diameter main combustion chamber (1), a one-way air flow path (9), and a B-type coated exchange-type reduced-diameter piston ( 22BB)
And an energy storage cycle engine-equipped device having a device driven by a rotational force. 83. A fuel injection valve (7B) and an igniter (8) that open to the reduced diameter main combustion chamber (1), a one-way air flow path (9), a B-type ceramic exchange type reduced diameter piston ( 2
2BC) and an energy storage cycle engine-mounted device having a device driven by rotational force. 84. A device mounted on an energy storage cycle engine, wherein a preheating ignition device (8A) is used instead of the ignition device (8). 85. The steam delivery solenoid valve (4A), steam injection solenoid valve (6A), fuel steam injection solenoid valve (7), steam injection solenoid valve (7A), fuel injection solenoid valve (7C), fuel water Of the injection solenoid valve (7D) and the water injection solenoid valve (7E),
An energy storage cycle engine-equipped device, wherein one or more magnet units are each composed of one or more electromagnets and two or more permanent magnets. 86. In the energy conservation cycle engine, a turbocharger (12) is provided in an exhaust duct (11) from the expanded combustion chamber (10), and supercharging is performed via an intake duct (13). Energy saving cycle engine equipment installed. 87. A device mounted on an energy storage cycle engine, wherein supercharging is performed by providing a rotary supercharger (14) in the air supply duct (13). 88. A device mounted on an energy conservation cycle engine, wherein the driving force of the rotary supercharger (14) is obtained from a crankshaft (16). 89. A starting motor / generator (17) is provided between the rotary supercharger (14) and the crankshaft (16) to enable the start including the rotary supercharger (14) and the storage of electricity. An energy storage cycle engine-mounted device characterized in that the device (28) can store electricity. 90. An energy storage cycle engine mounted device, wherein at least one of the input shaft (18) and the output shaft (19) of the starting motor / generator (17) can be shifted. 91. The steam delivery valve (4), the steam delivery solenoid valve (4A), the steam injection mushroom valve (6), the steam injection mushroom valve (6A), the fuel steam injection solenoid valve (7), and the steam injection solenoid. Valve (7A), fuel injection valve (7B), fuel injection solenoid valve (7C), fuel water injection solenoid valve (7D), water injection solenoid valve (7E), ignition device (8), preheating ignition device (8A) and An energy storage cycle engine, characterized in that at least one of the starting motor / generator (17) and the input shaft (18) and the output shaft (19) can be controlled by the energy storage cycle general controller (20). machine. 92. An energy storage cycle engine mounted device, wherein the energy storage cycle engine drives a ship. 93. An energy storage cycle engine-mounted device, wherein the energy storage cycle engine drives an aircraft. 94. A device equipped with an energy storage cycle engine, wherein the energy storage cycle engine drives a vehicle. 95. An energy storage cycle engine mounted device, wherein the energy storage cycle engine drives various wheels. 96. An energy storage cycle engine mounted device, wherein the energy storage cycle engine drives various machines. 97. An energy storage cycle engine mounted device, wherein the energy storage cycle engine is a general-purpose internal combustion engine. 98. A device mounted on an energy storage cycle engine, wherein the energy storage cycle engine is an internal combustion engine for power generation. 99. A device equipped with an energy storage cycle engine, wherein the energy storage cycle engine is an internal combustion engine for supplying heat and electricity. 100. A device mounted on an energy storage cycle engine, wherein said reduced-diameter main combustion chamber (1) is provided oppositely. 101. An energy storage cycle engine-mounted apparatus characterized in that said reduced-diameter main combustion chamber (1) is opposed to each other as a two-cycle combustion chamber and has a completely elastic collision reciprocating motion. 102. An energy storage cycle engine-mounted apparatus characterized in that said reduced-diameter main combustion chamber (1) is provided opposite to each other as a two-cycle combustion chamber, and has a full elastic collision opposed reciprocating motion. 103. An energy storage cycle engine-equipped device, wherein the configuration is such that the full elastic collision reciprocating motion, the configuration in which all moving parts rotate in the same direction, and the configuration as an energy storage cycle. 104. A device mounted on an energy storage cycle engine, wherein said device is configured to reciprocate in a completely elastic collision, and to have a configuration in which all moving portions rotate in the same direction. 105. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, wherein a rotary supercharger (14) is provided as a configuration in which a completely elastic collision reciprocating motion and a configuration in which all the moving parts rotate in the same direction. Energy saving cycle engine equipment equipped with extreme capabilities. 106. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, in which a completely elastic collision reciprocating motion and a configuration in which all the moving parts rotate in the same direction are provided. An energy storage cycle engine mounted device characterized by providing a solenoid valve (7C) to meet the extreme of small size. 107. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, in which a complete elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction are provided. A device mounted on an energy storage cycle engine, characterized in that: 108. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, a configuration in which a completely elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction. Energy conservation cycle engine equipment. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, a configuration in which a complete elastic collision reciprocating motion and a configuration in which all moving portions rotate in the same direction are provided. An energy-saving cycle engine-equipped device characterized in that it is used for various small-sized applications such as a brush cutter. 110. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate completely in a completely elastic collision and to configure all the moving parts to rotate in the same direction. 14) An energy storage cycle engine-equipped device characterized in that the energy storage cycle is provided for various uses that are close to small, such as for a brush cutter. 111. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, in which a completely elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction are provided. An energy storage cycle engine-equipped device characterized in that a fuel injection solenoid valve (7C) is provided for various small-sized applications such as a brush cutter. 112. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration in which a resilient collision reciprocates completely and a configuration in which all moving parts rotate in the same direction. An energy-saving cycle engine-equipped device for use in various types of small and medium-sized applications, such as for outboard motors, as a cycle. 113. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and to configure all the moving parts to rotate in the same direction. 14) An energy storage cycle engine-equipped apparatus characterized in that the energy storage cycle is provided for various uses close to small and medium-sized ones such as an outboard motor. 114. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration in which reciprocating motion is completely elastic collision and a configuration in which all moving parts are rotated in the same direction. A device equipped with an energy storage cycle engine, characterized in that a fuel injection solenoid valve (7C) is provided as a cycle and used for various uses close to small and medium-sized such as for outboard motors. 115. A turbocharger (12) and a rotary supercharger (12), wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and a configuration in which all moving parts rotate in the same direction. 14) An energy storage cycle engine-equipped device characterized in that the energy storage cycle is configured to be used for various uses close to small and medium-sized ones, such as a general-purpose engine. 116. A turbocharger (12) and a rotary supercharger (12) in which the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and all the moving parts rotate in the same direction. 14) A device equipped with an energy storage cycle engine, wherein a fuel injection solenoid valve (7C) is provided for various uses close to small and medium-sized ones such as a general-purpose engine as a configuration for providing an energy storage cycle. 117. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration in which a resilient collision reciprocates completely and a configuration in which all moving parts rotate in the same direction. Energy-saving cycle engine-equipped equipment characterized in that it is used for various applications close to small and medium-sized such as general-purpose engines as a cycle configuration. 118. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration in which reciprocating motion is completely elastically impacted and a configuration in which all moving parts rotate in the same direction. A device equipped with an energy storage cycle engine, characterized in that a fuel injection solenoid valve (7C) is provided as a cycle and used for various applications close to small and medium-sized, such as general-purpose engines. 119. A turbocharger (12) and a rotary supercharger (12) in which the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and all the moving parts rotate in the same direction. 14) An energy storage cycle engine-equipped apparatus characterized in that the energy storage cycle is provided for various uses close to a medium size, such as a conventional gasoline engine automobile. 120. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and to configure all the moving parts to rotate in the same direction. 14) An energy storage cycle engine-equipped device characterized in that a fuel injection solenoid valve (7C) is provided for various uses close to a medium size, such as a conventional gasoline engine automobile, as a configuration for providing an energy storage cycle by providing 14). 121. A turbocharger (12) and a rotary supercharger, wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision facing configuration and to configure all the moving parts to rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped device characterized in that the energy storage cycle is configured for various uses close to a medium size, such as a conventional gasoline engine vehicle. 122. A turbocharger (12) and a rotary supercharger, wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision opposition and a configuration in which all moving parts rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped apparatus characterized in that a fuel vapor injection solenoid valve (7) is provided as an energy storage cycle and used for various applications close to a medium size such as a conventional gasoline engine vehicle. 123. A turbocharger (12) and a rotary supercharger, wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision facing configuration and a configuration in which all moving parts rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped device characterized in that the energy storage cycle is configured for various near-medium-sized applications such as a conventional diesel engine vehicle. 124. A turbocharger (12) and a rotary supercharger, wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and a configuration in which all moving parts rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped apparatus characterized in that a fuel vapor injection solenoid valve (7) is provided as a configuration for an energy storage cycle, and the fuel vapor injection solenoid valve (7) is used for various applications close to a medium size such as a conventional diesel engine vehicle. 125. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is a configuration in which a resilient collision reciprocating motion and a configuration in which all moving portions rotate in the same direction are performed. 14) An energy storage cycle engine-equipped apparatus characterized in that the energy storage cycle is provided for various uses close to a medium size such as a conventional diesel engine vehicle. 126. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and configuration in which all moving parts rotate in the same direction. 14) An energy storage cycle engine mounted device characterized in that a fuel vapor injection solenoid valve (7) is provided for various uses close to a medium size such as a conventional diesel engine vehicle as a configuration for providing an energy storage cycle by providing 14). . 127. A turbocharger (12) and a rotary supercharger (12) in which a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and a configuration in which all moving parts rotate in the same direction. 14) An energy storage cycle engine-equipped apparatus characterized in that a fuel injection solenoid valve (7C) is provided for various uses close to a medium-sized one such as a diesel engine vehicle as a configuration for providing an energy storage cycle by providing 14). 128. A turbocharger (12) and a rotary supercharger (12) in which a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and a configuration in which all moving parts rotate in the same direction. 14) An energy storage cycle engine-equipped apparatus characterized in that the energy storage cycle is provided for various uses close to small and medium-sized ones such as small boats. 129. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and to configure all the moving parts to rotate in the same direction. 14) A fuel vapor injection solenoid valve (7) is provided to provide an energy conservation cycle engine, and the energy conservation cycle engine is characterized in that it is used for various uses close to small and medium-sized ones such as conventional small boats. machine. 130. The turbocharger (12) and the rotary supercharger (12) are configured such that the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision, and all the moving parts rotate in the same direction. 14) An energy storage cycle engine-equipped device characterized in that a fuel injection solenoid valve (7C) is provided for various uses close to small and medium-sized ones such as a conventional small ship as a configuration for providing an energy storage cycle by providing the energy storage cycle. . 131. A turbocharger (12) and a rotary supercharger in which the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and reciprocating motion in all the moving parts in the same direction. (14) is provided,
An energy storage cycle engine-mounted device characterized by being used for various uses close to small and medium-sized ones, such as those for small boats, as an energy storage cycle. 132. A turbocharger (12) and a rotary supercharger, wherein the core configuration of the energy conservation cycle engine is configured to reciprocate in a completely elastic collision and reciprocating motion in all the moving parts in the same direction. (14) is provided,
A device equipped with an energy storage cycle engine, characterized in that a fuel vapor injection solenoid valve (7) is provided as a configuration for the energy storage cycle, and the fuel vapor injection solenoid valve (7) is used for various uses close to small and medium-sized ones such as conventional small boats. 133. A turbocharger (12) and a rotary supercharger, wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and a configuration in which all moving parts rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped device characterized by providing a fuel injection solenoid valve (7C) as a configuration for the energy storage cycle and for various uses close to small and medium-sized, such as those for conventional small boats. 134. A turbocharger (12) and a rotary supercharger, wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision facing configuration and to configure all the moving parts to rotate in the same direction. (14) is provided,
An energy storage cycle engine-equipped device characterized by being used as an energy storage cycle for various uses such as power generation for large and medium-sized vehicles such as those for conventional medium and large vessels. 135. A turbocharger (12) and a rotary supercharger, wherein a core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision facing configuration and a configuration in which all moving parts rotate in the same direction. (14) is provided,
A fuel vapor injection solenoid valve (7) is provided as a configuration for the energy conservation cycle.
Equipment for energy conservation cycle engines characterized for various uses such as power generation close to medium size. 136. A turbocharger (12) and a rotary supercharger, wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and opposing configuration, and all the moving parts rotate in the same direction. (14) is provided,
As an energy conservation cycle, a fuel injection solenoid valve (7C) and a steam injection solenoid valve (7A) are provided for various uses such as power generation close to large / medium, such as those for conventional medium and large vessels. Energy conservation cycle engine equipment. 137. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and to configure all the moving parts to rotate in the same direction. 14) An energy storage cycle engine-equipped device characterized in that the energy storage cycle is configured to be used for various purposes such as power generation for large and nearly medium-sized vehicles such as those for conventional medium and large vessels. 138. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy storage cycle engine is configured to reciprocate in a completely elastic collision and to configure all the moving parts to rotate in the same direction. The fuel vapor injection solenoid valve (7) is provided as a configuration for providing an energy conservation cycle by providing the fuel vapor injection solenoid valve (14), which is characterized by being used for various purposes such as power generation close to a large / medium size such as a conventional medium-sized / large marine vessel. Energy conservation cycle organization. 139. A turbocharger (12) and a rotary supercharger (12) as a core configuration of the energy conservation cycle engine, wherein the configuration is such that a complete elastic collision reciprocating motion and the configuration in which all moving parts rotate in the same direction. 14) to provide a fuel injection solenoid valve (7C) and a steam injection solenoid valve (7A) as a configuration for energy conservation cycle, and for various applications such as power generation close to large / medium size such as conventional medium and large vessels An energy storage cycle engine-equipped device characterized by the following. 140. A device mounted on an energy storage cycle engine, wherein the combustion gas of the energy storage cycle engine is absorbed by a large amount of injected steam. 141. A device mounted on an energy storage cycle engine, wherein the combustion gas of the energy storage cycle engine is absorbed by a large amount of injected steam, and a chemical substance is mixed into water that becomes the steam. 142. A device mounted on an energy storage cycle engine, wherein the combustion gas of the energy storage cycle engine is absorbed by a large amount of injected steam, and a chemical is mixed into the water that becomes the steam. 143. A device mounted on an energy storage cycle engine, wherein the fuel burned by the energy storage cycle engine is any one of gasoline, light oil, heavy oil, hydrogen, natural gas, methanol, propane gas, alcohol and methane. . 144. The fuel burned in the energy storage cycle engine is used as a compression stroke from an end point of an intake stroke.
An energy storage cycle engine mounted device characterized in that it is stored in a reduced diameter main combustion chamber 1. 145. An energy storage cycle engine-equipped device characterized in that the configuration employed in the energy storage cycle engine is limited to a very small size and only complete elastic collision reciprocation is performed.