JP2000234536A - Energy reserving cycle engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To decrease NOx and increase an output by disposing a heat exchanger for a nearly percolation boiler serving a diameter contracting main combustion chamber as a final point, and timely injecting steam generated therein through a steam injection valve to a wall surface of the combustion chamber for a short time. SOLUTION: A pair of diameter enlarged piston 21 is continuously connected to a crankshaft 16, and each diameter enlarged piston 21 is fitted to a pair of cylinder heads 15 disposed opposing to each other. A fuel injection valve 7B and an ignition device 8 are provided to be faced to a diameter contracted main combustion chamber 1 partitioned to each cylinder head 15, and air injected from an air flow path 9 and fuel injection from a fuel injection valve 7B are agitated and mixed with each other to carry out ignition combustion. 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, and a wall surface of a combustion chamber is cooled, and thereby, NOx is decreased, and an output is increased. A turbo supercharger 12 is operated by exhaust energy, and steam is generated by a heat exchanger 2. A rotary supercharger 14 is operated by an electric motor 17 and the like to supercharger intake air.

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 the histone cycle, which converts the reciprocating motion of a piston into rotational power, by using the third law of mechanical energy conservation. 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 maximum combustion pressure is, for example, 3 at the crank angle after dead center.
The present invention relates to the addition and improvement of the mechanism of the energy saving cycle internal combustion engine of the prior application, in which the isolated combustion in the reduced diameter main combustion chamber is released after 0 degree to enhance the energy conversion efficiency and greatly improve the combustion.

[0002]

2. Description of the Related Art As conventional techniques, there are ordinary constant volume cycle engines and constant pressure cycle engines, which are used for driving various machines such as vehicles, ships and agricultural machines, and for supplying heat and electricity together. Prevention of global warming including reduction of CO2
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 essential. Therefore, in addition to a large increase in cooling loss, increasing the maximum combustion pressure results in a large increase in weight per unit output and friction loss.

[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. Ratio, the combustion pressure and the combustion temperature in addition to the thermal efficiency decrease, and the combustion pressure and the combustion temperature decrease sharply, and the combustion condition suddenly shifts to the worst.
Combustion that reduces x increases the unburned content, and combustion that reduces the unburned content increases NOx.

[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 make it to the extent, the weight per output becomes extremely large, it cannot be used for applications requiring light weight and large output such as automobiles, and if used forcibly, unburned fine particle pollution increases,
25% to 15% thermal efficiency for gasoline engines with faster combustion
There is a disadvantage that it is greatly reduced before and after.

[0005]

There is an urgent need to reduce pollution including CO2 reduction and global warming prevention. The present invention relates to a reciprocating motion of a piston as an energy conservation cycle that seeks the maximum use of the law of nature to the utmost. To increase the energy conversion efficiency of the piston cycle to greatly reduce pollution including CO2 reduction. The purpose is to add and improve the mechanism.

[0006]

SUMMARY OF THE INVENTION In view of the above-mentioned problems, the present invention provides various types of energy storage cycle internal combustion engines in place of conventional constant volume cycle engines and constant pressure cycle engines, in which it is difficult to reduce pollution including CO2 reduction. We will add and improve the mechanism to expand the engine from ultra-large to ultra-small and use it as an internal combustion engine for driving, general-purpose and power generation of ships, aircraft, vehicles, various wheels, various machines.

In the energy saving cycle internal combustion engine, as shown in FIG. 1, the two-stage combustion of the reduced-diameter main combustion chamber 1 and the expanded-diameter combustion chamber 10 is a large-advancing ignition timing, a constant-volume large-approach combustion, and an ultra-high-speed agitation combustion when the isolation is released. Since combustion is greatly improved, the mainstream is two cycles with a simple structure. In addition, the maximum combustion pressure at the same compression ratio is greatly increased by constant-volume large-approach combustion, and the speed-type energy + volume-type energy is used effectively. In order to reduce the diameter of the piston 21, the diameter of the piston 21 is increased by a very short stroke, a very high speed, and a simple structure of the crankshaft 16.
In the following, the D-type energy-storing cycle internal combustion engine will be described with the mainstream of direct drive, but it is not limited to the 2-cycle D-type energy-storing cycle internal-combustion engine, but is applied to various energy-storing cycle internal-combustion engines depending on the application.

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 combustion chamber having a significantly lower pressure than that of the prior art, and the expanded piston 21 is also greatly expanded. Ultra-short stroke with smaller piston stroke, higher revolution than conventional technology with the same piston diameter,
With the ultra-high-speed engine as the mainstream, the reduced-diameter main combustion chamber 1 having a certain volume or more and the reduced-diameter main combustion chamber 1 including the approximate once-through boiler-like heat exchanger 2 and the one-way air passage 9 disclosed in the earlier application.
The steam delivery valve 4, the steam delivery solenoid valve 4A, the steam injection mushroom valve 6, the steam injection solenoid mushroom valve 6A, the fuel steam injection solenoid valve 7, the steam injection solenoid valve 7A, the known fuel injection valve 7B, and the fuel injection solenoid valve 7C And solenoid valve 7D, water injection solenoid valve 7E, known ignition device 8, and preheating ignition device 8
A is appropriately added, and a new mechanism such as a control device is appropriately added to the configuration of the supercharging cycle including the turbocharger 12 and the rotary supercharger 14, and in the reduced-diameter main combustion chamber having a certain volume or less, , We will appropriately reduce the added configurations and mechanisms and add new ones as appropriate.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS ** An embodiment of the present invention will be described with reference to FIGS. 1 to 8. As shown in FIG. 1, an energy storage cycle internal combustion engine can be configured very simply.
The large-diameter combustion chamber can be made lighter by lowering the pressure, and in addition, the smaller the ratio of piston stroke S to the cylinder inner diameter S, S / D = 1/4, etc., the lighter the output and the greater the production cost per output. The energy-saving cycle internal combustion engine is capable of simultaneously achieving the extremes of light weight and large output, the extremes of manufacturing cost reduction, and the extreme reduction of CO2 reduction and prevention of global warming. In the process of adding various mechanisms to the ultra-small size, the explanation will be reinforced sequentially.

As described above, the energy saving cycle internal combustion engine shown in FIGS. 1 to 5 can be a high-power high-speed engine having a significantly larger number of revolutions than the prior art with the same cylinder inner diameter. Combustion can also be performed at a constant volume and large-close combustion with ignition timing significantly advanced compared to the conventional technology, so that the maximum combustion pressure at the same compression ratio can be greatly increased. The heat load of the expanded combustion chamber is greatly reduced, and the engine becomes a lightweight, high-output high-speed engine. Therefore, in the reduced-diameter main combustion chamber having a certain volume or more, the heat exchanger 2 and the steam injection device are used to increase the NOx reduction output. The heat exchanger 2 is a heat exchanger 2 like a once-through boiler using at least one steam pipe 3.
Preferably, a steam delivery valve 4 is provided at the end point of the steam guide pipe 3, and the steam delivery valve 4 can be opened in the steam reservoir 5 as needed.
The optimal opening / closing control is selectable, and the steam injection mushroom valve 6 and the fuel injection valve 7B are provided with the ignition device 8 so as to be able to timely open the reduced-diameter main combustion chamber 1, and the optimal opening / closing ignition control is selectable. The husband is appropriately connected to the energy conservation cycle general controller 20 shown in FIG. 8, and the air flow and the fuel injected from the one-way air flow path 9 are mixed and combusted, and the steam is appropriately injected to reduce NOx. Move closer.

Therefore, in FIG. 1 and FIG.
The fuel injection valve 7 that opens and closes and ignites the reduced-diameter main combustion chamber 1
B and an igniter 8 are provided, and the air injected from the one-way air flow path 9 and the fuel from the fuel injection valve 7B are mixed and agitated, ignited and burned by the igniter 8, and the steam is supplied in a timely manner to the steam pipe 3.
A predetermined amount of steam is injected from the outer periphery of the steam injection mushroom valve 6 toward the wall surface of the reduced-diameter main combustion chamber 1 via a steam delivery valve 4 and a steam reservoir 5 toward the wall surface of the reduced-diameter main combustion chamber 1 in a very short time, and has a large specific gravity. The wall surface is directly cooled by moisture or wet steam, radiant heat is converted to dry steam, NOx is reduced and output is increased by dry steam or the like, exhausted from the expanded combustion chamber 10 to the exhaust duct 11, and exhausted by exhaust energy. By operating the turbocharger 12, the supply pressure of the supply duct 13 is increased, and the direct or mechanical supercharger 1 is increased.
4 is operated to supply air to the expanded combustion chamber 10. During the operation of the rotary supercharger 14, the rotation of the crankshaft 16 is set as the rotation of the input shaft 18 and the output shaft 19 of the starting motor / generator 17 during the operation, and the rotation of the rotary supercharger 14 is appropriately performed. Electric power is 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 mechanical supercharger 1 is operated.
By rotating the crankshaft 4 and 4 and supplying air to the expanded combustion chamber 10, the internal combustion engine for energy conservation cycle is started. 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 point of the steam guiding pipe 3 so as to be openable and closable in the steam reservoir 5 of the steam injection solenoid mushroom valve 6A. Valve 6A
A fuel injection valve 7B and an ignition device 8 are 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 related art are agitated and mixed, and ignited by the ignition device 8. The reduced diameter main combustion chamber has a constant volume, large close-separation combustion, and the high-speed swirling steam injection from the outer circumference of the mushroom valve including the swirling blade 27 of the steam injection electromagnetic mushroom valve 6A. Exhaust to the exhaust duct 11 side. The magnets of the steam injection solenoid valve 6A and the steam delivery solenoid valve 4A have a permanent magnet 25 fixed to their respective valve rods 23 and an electromagnet 26 fixed to their respective valve boxes 24. The electromagnet 26 and two or more permanent magnets 25 constitute a magnet section.

[0013] Instead of the cylinder head 15 of FIG.
When the third embodiment of the cylinder head 15B is used, fuel and steam are injected into the reduced-diameter main combustion chamber 1 so that the fuel can be 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. Therefore, the maximum combustion pressure at the same compression ratio is greatly increased compared with the prior art by the constant-diameter main combustion chamber constant-volume close-separation combustion.
As NOx reduction and output increase combustion, the exhaust gas is exhausted from the expanded combustion chamber 10 to the exhaust duct 11 side. Fuel vapor injection solenoid valve 7
The permanent magnet 25 is fixed to each of the valve stems 23 and 23A, the electromagnet 26 is fixed to each of the valve boxes 24, and one or more electromagnets 26 and two or more permanent magnets 25 are provided. Constitutes the magnet section.

Instead of the cylinder head 15 of FIG. 1, FIG.
When the fourth embodiment of the cylinder head 15C is used, fuel and steam are injected into the reduced-diameter main combustion chamber 1 so as to be ignitable.
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. The maximum combustion pressure at the same compression ratio is greatly increased compared to the conventional technology by the constant-diameter main combustion chamber constant-volume close-separated combustion, and the steam injection, NOx reduction, and output from the steam injection solenoid valve 7A at the optimum time. As the increased combustion, the expanded combustion chamber 1
Exhaust from 0 to exhaust duct 11 side. The magnet parts of the steam injection solenoid valve 7A and the fuel injection solenoid valve 7C are
A permanent magnet 25 is fixed to 3 and 23, and an electromagnet 26 is fixed to each of the valve boxes 24. A magnet unit is constituted by one or more electromagnets 26 and two or more permanent magnets 25.

Instead of the cylinder head 15 of FIG. 1, FIG.
When the fifth embodiment of the cylinder head 15D is used, the fuel and steam are injected into the reduced-diameter main combustion chamber 1 so that they can be 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, or methanol, the mixture is stirred and mixed, and compression ignition is performed by the ignition device 8 or the preheating ignition device 8A.
The maximum combustion pressure at the same compression ratio is greatly increased from the conventional technology by the constant-diameter main combustion chamber constant-volume, large-volume close-separation combustion, and is expanded as steam injection, NOx reduction, and output increase combustion from the steam injection solenoid valve 7A at the optimum time. Exhaust from the radial combustion chamber 10 to the exhaust duct 11 side.

A description will be given of a case in which the cylinder head 15E of FIG. 6 is used instead of the cylinder head 15 of FIG. 1 according to the sixth embodiment. Fuel and water are injected into the reduced-diameter main combustion chamber 1. A fuel water injection solenoid valve 7D and an ignition device 8 are provided so as to be ignitable, and the air injected from the one-way air flow path 9 and the fuel injected from the fuel water injection solenoid valve 7D are agitated and mixed to form a known ignition. By igniting by the device 8, the maximum combustion pressure at the same compression ratio is greatly increased by the close compression combustion in the reduced diameter main combustion chamber as compared with the conventional technology, and the high pressure water in the water reservoir 5A is optimally discharged by the fuel water injection electromagnetic. As the water injection and NOx reduction combustion from the valve 7D, the exhaust gas is exhausted from the expanded combustion chamber 10 to the exhaust duct 11 side. The magnet portion of the fuel water injection solenoid valve 7D has a permanent magnet 25 fixed to one or more valve rods 23, 23A, an electromagnet 26 fixed to a valve box 24, and one or more electromagnets 26 and two or more The permanent magnet 25 forms the magnet section.

A description will be given of a case where a seventh embodiment of the cylinder head 15F shown in FIG. 7 is used instead of the first embodiment of the cylinder head 15 shown in FIG. 1. Fuel and water are injected into the reduced-diameter main combustion chamber 1. A water injection solenoid valve 7E, a fuel injection valve 7B, and an ignition device 8 are provided so as to be ignitable, and the air injected from the one-way air flow path 9 and the fuel injected from the fuel injection valve 7B are agitated and mixed. And the maximum combustion pressure at the same compression ratio is greatly increased compared with the prior art by the constant-diameter, large-volume close-separation combustion, and the water injection from the water injection solenoid valve 7E is performed at the optimum time. As NOx reduction combustion, the exhaust gas is exhausted from the expanded combustion chamber 10 to the exhaust duct 11 side. The magnet portion of the water injection solenoid valve 7E has a permanent magnet 25 fixed to the valve rod 23, an electromagnet 26 fixed to the valve box 24, and a magnet portion configured by one or more electromagnets 26 and two or more permanent magnets 25. To do.

The control device will be described with reference to FIG. 8. As a united control device, various control devices are built in the energy saving cycle general control device 20, and a sensing unit, a calculation unit, a regulation unit, and the like are included. Detect, calculate, and regulate the temperature, pressure, rotation speed, etc. of each part to reduce pollution and greatly increase thermal efficiency, including optimal combustion control. 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 vapor injection solenoid valve 7 or the steam injection solenoid valve 7A or the steam injection solenoid mushroom valve 6A or the steam injection mushroom valve 6 is reduced as NOx by performing optimal steam injection control based on detection calculation regulation and the like. To achieve almost no combustion / additional increase in steam energy additional output and constant-volume close-separation combustion to reduce pollution and greatly increase thermal efficiency. 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 high-speed water injection from the water injection solenoid valve 7D is reduced as optimal water injection control by detection calculation regulations and the like. Reduces pollution and increases thermal efficiency as large-diameter isolated combustion in the main diameter combustion chamber 1.

That is, the maximum combustion pressure at the same compression ratio is greatly increased as compared with the prior art by the constant-volume large-close-separation combustion in the reduced-diameter main combustion chamber 1, and the greatly increased heat energy is removed by the isolated combustion to expand the piston 21. High-speed injection to reduce ultra-high-speed pollution and eliminate reburning, and at the same time, dynamically expand the piston with dynamic pressure heat energy and static pressure heat energy to achieve the best rotational power conversion efficiency (90 degrees after dead center). Concentrating the heat energy release in the previous section, reduce the pollution and increase the thermal efficiency greatly, and operate the turbocharger 12 of the exhaust duct 11 from the expanded combustion chamber 10 to discharge the exhaust gas to the heat exchanger 2 side or directly to the atmosphere. The air discharged from the turbocharger 12 and sucked from the turbocharger 12 is supplied to the expanded combustion chamber 10 directly through the air supply duct 13 or by the rotary supercharger 14. Therefore, during operation, the mechanical supercharger 14 is operated by the rotational force of the crankshaft 16, and at the time of starting, the crankshaft 16 and the mechanical supercharger 14 are rotated by the starting motor / generator 17 to start. However, since various conditions change, such as when the outside air temperature ゃ stoppage or long-time operation,
In order to detect, calculate and regulate the temperature, the number of revolutions of each part, the amount of electricity stored in the electricity storage device 28, etc., the starting motor / generator 17, the input shaft 18 and the output shaft 19 are optimally rotated. A number of controls are used to make the controller suitable for starting and various operating conditions.

Referring to FIG. 9, when used as various types of engines, such as model airplanes, which are close to the extreme limit, the energy preservation cycle engine reverses the direction of motion of reciprocating motion and rotational motion to rapidly reduce kinetic energy. As a configuration that greatly reduces the loss of kinetic energy consumed, a configuration that performs a full elastic collision reciprocating motion and a configuration that all the moving parts rotate in the same direction are adopted. The energy conservation cycle method is used as a configuration that greatly reduces non-rotational release heat energy loss, which is a loss that increases the force that inhibits rotation, such as the force acting in the rotation direction. Has applied for a patent, but describes an example of adopting only a configuration that greatly reduces the loss of kinetic energy reduction, citing a small model airplane engine. That. In other words, when the energy conservation cycle system is not adopted, such as a small-sized model airplane engine that is close to the limit, a completely elastic collision reciprocating motion is adopted, and as shown in FIG. It is preferable that the dead center is also an explosion stroke, and it is a perfect elastic collision reciprocating motion. The supercharger is only the rotary supercharger 14 and is operably attached to the engine main body air supply duct 13.
It is good for kinetic energy reduction and loss reduction, and others use conventional technology as needed.

Referring to FIG. 10, when used as a D-type energy storage cycle engine for various small-sized applications such as a brush cutter, the energy storage cycle engine has a configuration that greatly reduces kinetic energy reduction loss. An energy-conserving cycle system is adopted as a configuration that performs full elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction. The energy storage cycle method, the fully elastic collision reciprocating movement method, and the method in which all moving parts rotate in the same direction will be described. That is, D for the brush cutter
In the case of a combined use of the energy storage cycle system, the fully elastic collision reciprocating motion system, and the system in which all the moving parts rotate in the same direction, such as a type energy storage cycle engine, as shown in FIG. Both the dead center and the left dead center have a full elastic collision reciprocating motion with an explosion stroke, and the supercharger is only a rotary supercharger 14 and is operably attached to the engine main body air supply duct 13.
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 the pressure gas as it is, the fuel injection valve ends injection from the end point of the suction stroke to the first half of the compression stroke, and the other conventional technology is used as needed.

Referring to FIGS. 1 and 10, when used as a D-type energy conservation cycle engine for various uses close to small and medium-sized ones, such as for an outboard motor, the energy conservation cycle engine has a kinetic energy reduction loss. As a configuration for greatly reducing the energy, a configuration in which the reciprocating motion of a completely elastic collision and a configuration in which all the moving parts rotate in the same direction are adopted. The energy saving cycle method, the fully elastic collision reciprocating movement method, and the method in which all the moving parts rotate in the same direction will be described. 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. Thus, as a two-stroke double-headed piston, the right dead center and the left dead center are both in an explosion stroke, a completely elastic collision reciprocating motion, and the supercharger is only the rotary supercharger 14 or the turbocharger 12 Operable as the engine air supply duct 13 and the exhaust duct 1
The turbocharger 12 is attached to the fuel injection valve 1 to reduce the kinetic energy loss and increase the thermal efficiency. The fuel injection timing in the reduced-diameter main combustion chamber 1 is set between the end point of the intake stroke and the end point of the compression stroke. The injection gas is appropriately selected in accordance with the injection pressure.For example, when injecting a fuel gas such as propane gas into the fuel injection valve as it is, the injection is completed from the end point of the suction stroke to the first half of the compression stroke, and the other conventional technology is used as needed. Use

Referring to FIG. 1 and FIG. 10, when used as a D-type energy storage cycle engine for various uses close to a small or medium-sized one such as a general-purpose engine, the energy storage cycle engine has a large kinetic energy reduction loss. As a configuration to reduce, a configuration that makes a full elastic collision reciprocating motion and a configuration that all the moving parts make a rotational motion in the same direction are adopted,
As a configuration for greatly reducing the non-rotation release heat energy loss, an energy storage cycle system is adopted, and an energy storage cycle system, a completely elastic collision reciprocating motion system, and a system in which all the moving parts rotate in the same direction will be described. .
That is, as shown in FIG. 1 and FIG. 10, when the energy storage cycle system such as a D-type energy storage cycle engine for a general-purpose engine, the fully elastic collision reciprocating system, and the system in which all the moving parts rotate in the same direction are used. In addition, as a two-cycle double-headed piston, a completely elastic collision reciprocating motion in which both the right dead center and the left dead center have an explosion stroke, and the supercharger is only the rotary supercharger 14 or the turbocharger 12 As a combined use, the turbocharger 12 is operably attached to the air supply duct 13 and the exhaust duct 11 for reducing the kinetic energy reduction loss and increasing the thermal efficiency, and the fuel injection timing in the reduced diameter main combustion chamber 1 is improved. From the suction stroke end point to the compression stroke end point, appropriately select according to the fuel injection pressure, for example, when injecting a fuel gas such as propane gas, the fuel injection valve as it is, Injection ended up first half of the compression stroke than input stroke end point, the condensation 径主 combustion chamber above a certain volume,
The combustion chamber of the steam internal combustion engine is used as needed.

Referring to FIG. 1 and FIG. 11, when used as D-type and E-type energy conservation cycle engines for various near-medium-sized applications such as conventional gasoline engine automobiles, the energy conservation cycle engines reduce kinetic energy. As a configuration for greatly reducing the loss, and as a configuration for greatly reducing the non-rotational release heat energy loss, a fully elastic collision reciprocating motion system, a fully elastic collision opposing reciprocating motion system, a system in which all moving parts rotate in the same direction, and Energy conservation cycle system is adopted. That is, in the case of a conventional D-type and E-type energy conservation cycle engine for a gasoline engine automobile, a combination of an energy conservation cycle system, a fully elastic collision reciprocating motion system, and a system in which all motion parts rotate in the same direction is used. -As shown in Fig. 11, a D-type or a D-type, in which both the right dead center and the left dead center have an explosion stroke, are provided opposite each other as a two-cycle double-headed piston to achieve a large reduction in vibration.
A fully elastic collision reciprocating motion or a fully elastic collision opposing reciprocating motion as a type energy storage cycle engine, and the supercharger is operable in combination with the rotary supercharger 14 and the turbocharger 12 to enable the engine to operate. Attaching the turbocharger 12 to the main body air supply duct 13 and the exhaust duct 11 is good for reducing the kinetic energy loss and increasing the thermal efficiency, and the fuel injection timing in the reduced diameter main combustion chamber 1 is compressed from the end point of the intake stroke. Until the end point of the stroke, an appropriate selection is made in accordance with the fuel injection pressure.For example, when injecting a fuel gas such as propane gas into the fuel injection valve as it is, the injection is performed from the end point of the intake stroke to the first half of the compression stroke. The closed main combustion chamber with a certain volume or more will be switched to the steam internal combustion engine combustion chamber as needed.

Referring to FIGS. 1 and 11, when used as a D-type and E-type energy conservation cycle engine for various uses close to a medium size such as a conventional diesel engine automobile,
The energy conservation cycle engine is designed to greatly reduce the kinetic energy reduction loss and to greatly reduce the non-rotationally released heat energy loss. Adopts the method of rotating in the same direction and the energy conservation cycle method. That is, in the case of a conventional D-type and E-type energy storage cycle engine for a diesel engine vehicle, when the energy storage cycle system, the fully elastic collision reciprocating motion system, and the system in which all the moving parts rotate in the same direction are used together, FIG. -As shown in Fig. 11, as a two-cycle double-headed piston, a D-type or a D-type in which both the right dead center and the left dead center have an explosion stroke is provided oppositely to greatly reduce vibration.
As an E-type energy conservation cycle engine, a fully elastic collision reciprocating motion or a fully elastic collision opposing reciprocating motion,
As the turbocharger is used together with the rotary supercharger 14 and the turbocharger 12, the turbocharger 12 is operably attached to the supply duct 13 and the exhaust duct 11 of the engine to reduce kinetic energy. Good for reducing loss and increasing thermal efficiency, the fuel injection timing in the reduced-diameter main combustion chamber 1 is appropriately selected according to the fuel injection pressure between the end point of the intake stroke and the end point of the compression stroke. When injecting the fuel gas directly into the fuel injection valve, the injection is completed from the end point of the intake stroke to the first half of the compression stroke, and the reduced-diameter main combustion chamber with a certain volume or more is used as the steam-internal combustion combined engine combustion chamber as needed.

Referring to FIG. 1 and FIG. 11, when used as D-type and E-type energy conservation cycle engines for various uses close to small and medium-sized ones, such as conventional small boats, the energy conservation cycle engines have kinetic energy 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. In other words, the D-type and E-type energy storage cycle engines for various applications such as conventional small boats, such as the energy storage cycle system, the fully elastic collision reciprocating motion system, and the system in which all the motion parts rotate in the same direction are used in combination. In this case, as shown in FIG. 1 and FIG. 11, a D-type or a D-type in which a right dead center and a left dead center have an explosion stroke as a two-cycle double-headed piston are provided to oppose each other to greatly reduce vibration. The storage cycle engine is a fully elastic collision reciprocating motion or a fully elastic collision opposing reciprocating motion, and the supercharger is operable in combination with the rotary supercharger 14 and the turbocharger 12 so that the engine body can be operated. Attaching the turbocharger 12 to the air duct 13 and the exhaust duct 11 is good for reducing the loss of kinetic energy and increasing the thermal efficiency, and the fuel injection timing in the reduced-diameter main combustion chamber 1 ends the suction stroke. In more until the end of the compression stroke point, selected appropriately according to the fuel injection pressure,
For example, when injecting a fuel gas such as propane gas directly into the fuel injection valve, the injection is completed from the end of the suction stroke to the first half of the compression stroke. It will be a combustion chamber.

Referring to FIG. 1 and FIG. 11, for various applications such as power generation for large and nearly medium-sized vehicles such as those for conventional medium-sized and large-sized ships,
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. As
With the full elastic collision reciprocating motion or the full elastic collision opposing reciprocating motion, the supercharger is operably used in combination with the rotary supercharger 14 and the turbocharger 12, and the engine main body air supply duct 13 and Turbocharger 12 in exhaust duct 11
Is good for reducing the kinetic energy 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 between the end point of the intake stroke and the end point of the compression stroke. For example, when injecting a pressure gas such as propane gas into the fuel injection valve as it is, the injection is completed from the end point of the suction stroke to the first half of the compression stroke. It is a combustion chamber of an internal combustion engine.

[0028]

According to the present invention, the configuration described above is added, and the following effects can be obtained. 1. The control of the energy conservation cycle engine is facilitated by adding the energy conservation cycle general control device. 2. Since various solenoid valves are added, overall control of the energy storage cycle is possible or easy. 3. Since the steam delivery solenoid valve and the steam injection solenoid valve are added, the steam injection can be concentrated at the optimum time, so that the pollution including NOx and the thermal efficiency can be easily reduced. 4. The addition of a steam delivery solenoid valve and a steam injection solenoid mushroom valve makes it possible to uniformly cool the reduced diameter main combustion chamber and increase the amount of injected steam, making it the optimal reduced diameter main combustion chamber as a hydrogen fuel combustion chamber. Can be. 5. The addition of the energy saving cycle general control device makes it easy to drive various vessels, various aircraft, various vehicles, various wheels, various machines, various generators, and as various general-purpose energy storage cycle engines. 6. The addition of the energy conservation cycle control device makes it easy to control the combustion of gasoline, light oil, heavy oil, propane, hydrogen, natural gas, methanol, etc. 7. The most important losses of the energy conservation cycle engine are the non-rotational heat energy loss and the kinetic energy reduction loss. In addition, it has been clarified that all the moving parts adopt the configuration of rotating in the same direction, thereby facilitating research and development for various applications.

[Brief description of the drawings]

FIG. 1 is a schematic overall configuration diagram showing a first example of an energy conservation cycle engine of the present invention, and is shown in a partial cross section.

FIG. 2 is a partially schematic sectional view showing a cylinder head 15A of a second embodiment of the cylinder head 15 of FIG.

FIG. 3 is a partially schematic sectional view showing a cylinder head 15B of a third embodiment of the cylinder head 15 of FIG.

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

FIG. 5 is a partially schematic sectional view showing a cylinder head 15D of a fifth embodiment of the cylinder head 15 of FIG.

FIG. 6 is a partially schematic sectional view showing a cylinder head 15E of a sixth embodiment of the cylinder head 15 of FIG. 1;

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

FIG. 8 is an overall configuration diagram for explaining the outline of the overall control system for various energy storage cycles of the present invention.

FIG. 9 is a schematic overall configuration diagram showing a second example of the energy storage cycle engine of the present invention, which is partially shown in section.

FIG. 10 is a schematic overall configuration diagram showing a third example of the energy storage cycle engine of the present invention, and is partially shown in section.

FIG. 11 is a schematic overall configuration diagram showing a fourth example of the energy storage cycle engine of the present invention, and is partially shown in section.

[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, 23, stem, 23A, 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) F02B 47/04 F02B 47/04 75/28 75/28 DB F02M 21/02 F02M 21/02 N 25 / 032 25/02 C 25/022 HF term (reference) 3G005 DA04 DA05 EA06 EA16 EA19 EA23 FA37 3G023 AA02 AB01 AB07 AC03 AC04 AC05 AC06 AC07 AD02 AD03 AD26 AD29 AF02 AF03 3G092 AA01 AA03 AA06 AA07 AA18 AB02 AB03 AB05 AB03 AB05 AC05 AC09 AC10 DB02 DB03 DB05 DD09 DE03S FA24 FA50

Claims (62)

[Claims] An approximate once-through boiler-like heat exchanger (2) ending at a reduced diameter main combustion chamber (1) is provided, and a steam delivery valve (4) is provided at an ending point of the steam guide pipe (3). Steam reservoir (5)
The steam reservoir (5) is provided with a steam injection mushroom valve (6A) in the reduced-diameter main combustion chamber (1) so that it can be opened in a timely manner.
An energy preserving cycle engine in which the reduced-diameter main combustion chamber (1) is provided with a fuel injection valve (7B) and an igniter (8) which are opened and operated as needed, and performs agitated combustion by a jet from a one-way air flow path (9). . 2. An approximate once-through boiler-like heat exchanger (2) having the reduced-diameter main combustion chamber (1) as an end point is provided, and a steam delivery solenoid valve (4A) is provided at an end point of the steam guide pipe (3). The steam injection solenoid valve (6) can be opened to the steam reservoir (5) in a timely manner, and the steam reservoir (5) can be opened in the reduced-diameter main combustion chamber (1) in a timely manner.
A), and a fuel injection valve (7B) and an igniter (8), which are opened and operated in a timely manner, are provided in the reduced-diameter main combustion chamber (1), and agitated combustion is performed by a jet from a one-way air passage (9). Energy conservation cycle organization to perform. 3. An approximate once-through boiler-like heat exchanger (2) having the reduced-diameter main combustion chamber (1) as an end point, and a steam delivery solenoid valve (4A) provided at an end point of the steam guide pipe (3). The steam injection solenoid valve (6A) and the swirl vane (6A) can be opened to the steam reservoir (5) in a timely manner. 27), and the fuel injection valve (7) which is opened in the reduced-diameter main combustion chamber (1) as appropriate.
B) and an ignition device (8), an energy storage cycle engine that performs agitated combustion by a jet from a one-way air flow path (9). 4. An approximate once-through boiler-like heat exchanger (2) having a reduced-diameter main combustion chamber (1) as an end point is provided, and a fuel / steam injection solenoid valve (7) is provided at an end point of the steam guide pipe (3). Is provided so as to be able to open to the reduced-diameter main combustion chamber (1) in a timely manner, and an igniter (8) that is operated in a timely manner is provided in the reduced-diameter main combustion chamber (1). An energy conservation cycle engine that performs agitated combustion by a jet of water. 5. An approximate once-through boiler-like heat exchanger (2) having the reduced-diameter main combustion chamber (1) as an end point, and a steam injection solenoid valve (7A) provided at an end point of the steam guide pipe (3). The fuel injection solenoid valve (7C) and the igniter (8), which can be opened in the reduced-diameter main combustion chamber (1) in a timely manner, are provided in the reduced-diameter main combustion chamber (1), and the unidirectional air flow is provided. An energy conservation cycle engine that performs agitated combustion by a jet from a road (9). 6. An approximate once-through boiler-like heat exchanger (2) having the reduced-diameter main combustion chamber (1) as an end point, and a steam injection solenoid valve (7A) provided at an end point of the steam guide pipe (3). A fuel injection valve (7B) and an igniter (8), which are opened in the reduced-diameter main combustion chamber (1) in a timely manner, are provided in the reduced-diameter main combustion chamber (1), and a one-way air flow path is provided. (9) An energy conservation cycle engine that performs stirring combustion by the jet from (9). 7. A fuel water injection solenoid valve (7D) is provided in the reduced-diameter main combustion chamber (1) so that it can be opened to the reduced-diameter main combustion chamber (1) in a timely manner. An energy conservation cycle engine provided with a fuel injection valve (7B) and an igniter (8) that are operated to perform an agitated combustion by a jet from a one-way air flow path (9). 8. A water injection solenoid valve (7) is provided in the reduced diameter main combustion chamber (1).
E) to make it possible to open the reduced-diameter main combustion chamber (1) in a timely manner,
An energy preserving cycle engine in which the reduced-diameter main combustion chamber (1) is provided with a fuel injection valve (7B) and an igniter (8) which are opened and operated as needed, and performs agitated combustion by a jet from a one-way air flow path (9). . 9. The energy storage cycle engine according to claim 1, wherein a preheating ignition device (8A) is used instead of the ignition device (8). 10. A steam delivery solenoid valve (4A), a steam injection solenoid valve (6A), a fuel steam injection solenoid valve (7), a steam injection solenoid valve (7A), a fuel injection solenoid valve (7C), and fuel water. Of the injection solenoid valve (7D) and water injection solenoid valve (7E),
The energy storage cycle engine according to any one of claims 1 to 9, wherein the at least one magnet unit includes at least one electromagnet and at least two permanent magnets. 11. The energy storage cycle engine according to claim 1, wherein the reduced-diameter main combustion chambers (1) are provided to face each other. 12. An energy storage cycle internal combustion engine according to claim 1, wherein a turbocharger (12) is provided in an exhaust duct (11) from the enlarged combustion chamber (10). An energy conservation cycle engine for supercharging via an air supply duct (13). 13. The energy storage cycle engine according to claim 1, wherein a supercharger is provided by providing a rotary supercharger (14) in the air supply duct (13). . 14. The system according to claim 1, wherein the driving force of the rotary supercharger is obtained from a crankshaft.
14. The energy storage cycle engine according to any one of claims 13 to 13. 15. A starting motor / generator (17) is provided between the rotary supercharger (14) and the crankshaft (16) to enable starting including the rotary supercharger (14) and to store electricity. 2. The device according to claim 1, wherein the device is capable of storing electricity.
15. The energy conservation cycle engine according to any one of claims 14 to 14. 16. The energy storage cycle engine according to claim 1, wherein the fuel used is any one of gasoline, light oil, heavy oil, hydrogen, natural gas, methanol, and propane. . 17. The apparatus according to claim 1, wherein at least one of an input shaft (18) and an output shaft (19) of said starting motor / generator (17) can be shifted. Energy conservation cycle engine according to paragraph. 18. The steam delivery valve (4), the steam delivery solenoid valve (4A), the steam injection mushroom valve (6), the steam injection solenoid 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 17. An energy storage cycle general controller (20) for controlling at least one of a starting motor / generator (17) and an input shaft (18) and an output shaft (19). An energy storage cycle engine according to any one of the preceding claims. 19. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine drives a ship. 20. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine drives an aircraft. 21. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine drives a vehicle. 22. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine drives various wheels. 23. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine drives various machines. 24. The energy storage cycle engine according to claim 1, wherein the energy storage cycle engine is a general-purpose internal combustion engine. 25. The energy storage cycle engine according to claim 1, wherein the internal combustion engine is a power generation internal combustion engine.
An energy storage cycle engine according to any one of the preceding claims. 26. An energy storage cycle engine, wherein the core has a configuration in which reciprocating motion is completely elastically impacted, a configuration in which all moving parts rotate in the same direction, and a configuration in which an energy storage cycle is provided. . 27. An energy preservation cycle engine, wherein the core is configured to reciprocate in a completely elastic collision and the configuration is such that all moving parts rotate in the same direction. 28. A model airplane provided with a rotary supercharger (14) as a core configuration of the energy conservation cycle engine, a configuration in which reciprocating motion is completely elastic collision, and a configuration in which all moving parts are rotated in the same direction. An energy conservation cycle engine that has been adapted to the extremely small size of applications. 29. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, in which a full elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction are provided. An energy conservation cycle engine equipped with a solenoid valve (7C) for miniature extremes, such as for model airplanes. 30. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, wherein a rotary elastic turbocharger (14) is provided 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. An energy conservation cycle engine characterized in that: 31. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine, wherein a rotary elastic supercharger (14) is provided as a configuration in which reciprocating motion is completely elastically impacted and a configuration in which all moving parts are rotated in the same direction. An energy conservation cycle engine characterized in that: 32. An energy-saving cycle, wherein a rotary supercharger (14) is provided as a core structure of the energy-saving cycle engine as a configuration of reciprocating motion with perfect elastic collision and a configuration of rotating all the moving parts in the same direction. An energy storage cycle engine characterized by being used for various small-sized applications such as a brush cutter. 33. A turbocharger (12) and a rotary supercharger (12), wherein the core configuration of the energy conservation 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 characterized by having an energy storage cycle for use in various small-sized applications such as a brush cutter. 34. 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 rotate in the same direction. An energy preservation cycle engine characterized in that a fuel injection solenoid valve (7C) is provided for various small-sized applications such as a brush cutter. 35. 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 conservation cycle engine characterized in that the cycle is configured for various uses close to small and medium-sized such as for outboard motors. 36. 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) to provide an energy conservation cycle for small outboard motors
An energy conservation cycle engine characterized by being used for various applications close to medium-sized. 37. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration of reciprocating motion with complete elastic collision and a configuration in which all moving parts rotate in the same direction. An energy preservation cycle engine characterized by providing a fuel injection solenoid valve (7C) as a cycle for various uses close to small and medium-sized such as for outboard motors. 38. 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 to configure all the moving parts to rotate in the same direction. 14) An energy storage cycle engine characterized in that the energy storage cycle is provided for various uses close to small and medium-sized ones such as general-purpose engines. 39. 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) to provide an energy conservation cycle, the fuel injection solenoid valve (7
C) An energy conservation cycle engine characterized in that it is used for various purposes close to small and medium-sized ones, such as general-purpose engines. 40. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration of reciprocating motion with complete elastic collision and a configuration in which all moving parts rotate in the same direction. An energy conservation cycle engine characterized by its use as a cycle for a variety of applications close to small and medium-sized engines such as general-purpose engines. 41. A rotary supercharger (14) is provided as a core configuration of the energy storage cycle engine as a configuration in which full elastic collision reciprocating motion and a configuration in which all moving parts rotate in the same direction are provided. An energy preservation cycle engine characterized by providing a fuel injection solenoid valve (7C) as a cycle for various uses close to small and medium-sized ones such as general-purpose engines. 42. 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 all the moving parts rotate in the same direction. 14) An energy storage cycle engine characterized in that the energy storage cycle is provided for various uses close to a medium size, such as a conventional gasoline engine automobile. 43. A turbocharger (12) and a rotary supercharger (12) as a core configuration of the energy storage 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 are performed. 14) to provide an energy conservation cycle, the fuel injection solenoid valve (7
C) An energy storage cycle engine characterized by being provided for various uses close to a medium size, such as a conventional gasoline engine car. 44. 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) An energy storage cycle engine characterized in that the energy storage cycle is configured for use in various medium-sized applications such as a conventional gasoline engine vehicle. 45. 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. An energy storage cycle engine characterized in that the fuel vapor injection solenoid valve (7) is provided for various uses close to a medium size, such as a conventional gasoline engine vehicle, as a configuration for providing an energy storage cycle by providing (14). 46. 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 reciprocating motion, and all the moving parts rotate in the same direction. (14) An energy storage cycle engine characterized in that the energy storage cycle is configured for use in various near-medium-sized applications such as a conventional diesel engine vehicle. 47. 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 opposition and configuration in which all moving parts rotate in the same direction. (14) An energy storage cycle engine characterized by providing a fuel vapor injection solenoid valve (7) as an energy storage cycle and providing a fuel vapor injection solenoid valve (7) for various uses close to a medium size such as a conventional diesel engine vehicle. 48. 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 characterized in that the energy storage cycle is provided for various uses close to a medium size such as a conventional diesel engine vehicle. 49. 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 characterized in that a fuel vapor injection solenoid valve (7) 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. 50. 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) to provide an energy conservation cycle, the fuel injection solenoid valve (7
C) is an energy conservation cycle engine characterized by being used for various applications close to a medium size such as a conventional diesel engine vehicle. 51. A turbocharger (12) and a rotary supercharger (12) as a core configuration of the energy storage 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 are performed. 14) An energy storage cycle engine characterized in that the energy storage cycle is provided for various uses close to small and medium-sized ones such as conventional small boats. 52. 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 characterized by providing a fuel vapor injection solenoid valve (7) as an energy storage cycle and providing a fuel vapor injection valve (7) for various uses close to small and medium-sized ones such as conventional small boats. 53. 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) to provide an energy conservation cycle, the fuel injection solenoid valve (7
C) An energy conservation cycle engine characterized by being provided for various uses close to small and medium-sized ones such as conventional small boats. 54. 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 reciprocating motion in all the moving parts in the same direction. (14) An energy storage cycle engine characterized in that the energy storage cycle is configured for use in various applications close to small and medium-sized ones, such as those for conventional small boats. 55. 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. An energy storage cycle engine characterized in that the fuel vapor injection solenoid valve (7) is provided for various uses close to small and medium-sized ones such as conventional small boats as a configuration for providing an energy storage cycle by providing (14). . 56. 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 reciprocating motion in all the moving parts in the same direction. An energy storage cycle engine characterized in that the fuel injection solenoid valve (7C) is provided for various uses close to small and medium-sized ones such as conventional small boats as a configuration for providing an energy storage cycle by providing (14). 57. 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) An energy conservation cycle engine characterized in that the energy conservation cycle is configured for use in various applications such as power generation for large and nearly medium-sized vehicles such as those for conventional medium and large vessels. 58. 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. The fuel vapor injection solenoid valve (7) is provided as a configuration for providing an energy conservation cycle by providing (14), and is characterized by being used for various uses such as power generation close to a large / medium size such as a conventional medium / large ship. Energy conservation cycle organization. 59. 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. The fuel injection solenoid valve (7C) and the steam injection solenoid valve (7A) are provided as a configuration for providing an energy conservation cycle by providing (14), and various uses such as power generation for large and medium-sized vehicles such as conventional medium-sized and large-sized ships are provided. An energy conservation cycle engine characterized by: 60. 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 characterized in that the energy storage cycle is provided for a variety of uses such as power generation for large and nearly medium-sized vehicles such as those for conventional medium and large vessels. 61. 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. 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. 62. 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) to provide an energy conservation cycle, the fuel injection solenoid valve (7
C) and a steam injection solenoid valve (7A) provided for use in various applications such as power generation for large and nearly medium-sized vehicles such as those for conventional medium- and large-sized ships.