JPH1089075A - Device and method for making pendulum piston to serve as energy preserving cycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase a compression ratio and realize improvement of output in a device in which a crankshaft is rotated through a pendulum arm by the reciprocating motion of a double-end diameter enlarged piston, by arranging cams for retaining the intermediate part and one end of the pendulum arm on the double-end enlarged piston side and a main body side. SOLUTION: Two double-end diameter enlarged pistons are fitted to a pair of cylinders oppositely arranged, and the head parts of these double-end diameter enlarged pistons are formed into an appropriate recessed part, thereby a diameter enlarged combustion chamber is partitioned. Diameter contracted pistons are projected from the approximately centers of the appropriate recessed parts of these diameter enlarged pistons, so that a diameter contracted main combustion chamber can be partitioned, and combustion gas can be injected at a super high speed from the diameter contracted main combustion chamber when the isolation of the diameter enlarged pistons is released. Annular uneven parts 5... which are perpendicular to a piston moving direction are arranged in the peripheral surface of the diameter contracted piston, and also a noise reducing groove 11 slantly extended is arranged in the projected part at an end. Then, a pendulum arm is engaged with and retained in a pendulum hole 6 arranged in an approximately center between the double-end diameter enlarged pistons through a cam, and the swinging motion of the pendulum arm is transmitted to a crankshaft 25.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention employs a pendulum motion crank mechanism to increase the energy conversion efficiency of converting the reciprocating motion of a piston into rotational power, and utilizes the law of conservation of mechanical energy to achieve a dead center. For the subsequent predetermined period, the isolated combustion in the reduced-diameter main combustion chamber, for example, reduced to one fifth or the like, reduces the amount of energy used near the dead center (piston stroke volume) to save fuel and increase fuel consumption. The thermal energy of the part is greatly increased (by pressure increase) due to the savings, and when the isolation is released (30 ° to 7 ° crank angle after dead center)
0 °) and approaching the maximum combustion pressure, 6
An energy preservation cycle that substantially increases the rotational power of the energy conversion efficiency around 0 ° (hereinafter, crank angle is omitted) before and after the first half of the perfect aircraft (see FIG. 1B), and at the same time reduces the pollution as near constant volume combustion. Apparatus and method.

[0002]

2. Description of the Related Art An outline of Japanese Patent Application No. 7-79292 (first application) is that energy conversion is mainly performed by injecting isolated combustion water mainly in a reduced diameter main combustion chamber among means for making an ordinary reciprocating piston cycle an energy storage cycle. This is to provide an adiabatic non-cooled engine with a large-diameter combustion chamber as a low-temperature and low-pressure combustion chamber by large conversion to low-temperature superheated steam. Japanese Patent Application No. 8-272
The outline of 07 (second application) is a special invention of the inverted pendulum piston cycle with various types of energy conservation cycles. The outline of Japanese Patent Application No. 8-78414 (third application claiming priority) describes the main parts for making a normal reciprocating piston cycle an energy conservation cycle. The outline of Japanese Patent Application No. 8-122114 (Fourth priority application) provides a method and apparatus for making a normal reciprocating piston cycle an energy conservation cycle. Japanese Patent Application No. 8-172
The summary of 752 (Fifth Priority Application) provides a method and apparatus for using a special invention pendulum piston as an energy conservation cycle. Therefore, in each case, the isolated combustion in the reduced-diameter main combustion chamber whose diameter has been appropriately reduced causes the dead center or 3% after the dead center.
In the worst case of the rotational power conversion efficiency near 0 °, the thermal energy is greatly increased by saving the savings (the pressure is greatly increased with a small amount of fuel), and as the large rotational force near the first half of the ideal machine of the rotational power conversion efficiency, Along with greatly increasing the thermal efficiency, we aim to greatly reduce pollution by approximating constant volume combustion and combustion at the time of release of isolation.

[0003]

As described above, when the energy storage cycle is used, in addition to being able to greatly reduce pollution while greatly increasing thermal efficiency, an unlimited number of configurations are possible, so that many configurations are provided. We have continued our invention, especially because the pendulum piston crank mechanism has a simple structure and can be small, light and large. That is, the reciprocating piston crank mechanism has a very poor power conversion efficiency at the dead center or around 30 ° after the dead center. In the conventional technology, this portion has the maximum heat energy (heat energy higher than the compression pressure).
Because almost all of the heat is consumed, most of the heat energy is used to increase frictional loss, etc., and heat energy is almost completely eliminated in the prime mover of power conversion efficiency, and the heat efficiency is greatly reduced. Since the chamber volume suddenly increases, the combustion becomes extremely non-constant volume combustion at low pressure and low temperature, and the combustion suddenly shifts to the worst combustion condition combustion. Therefore, when the unburned combustion is reduced, the combustion becomes NOx increased. Increased combustion,
Exhaust gas pollution is greatly increased, thermal efficiency is greatly reduced, and there are the usual challenges of hitting technology barriers.

Accordingly, the present invention is directed to an apparatus and a method for performing an energy preservation cycle in which the diameter is reduced to, for example, one-fifth (hereinafter referred to as 5), limited to a portion near a dead center as shown in FIGS.
As an example of reduced combustion in the main combustion chamber with reduced diameter (FIG. 1A, FIG. 2A, and FIG. 3A), energy use near the dead center (stroke volume of the piston) is reduced to 25 minutes. As a necessary minimum, the fuel consumption is reduced as much as possible, and most of the heat energy, for example, 24/25, is greatly increased (large pressure increase) by the savings, and the diameter is reduced at the optimal time after the dead center. Release isolated combustion in the main combustion chamber, for example, 60 ° after dead center
Moving the maximum thermal energy usage or the maximum bearing load back and forth, except for a micro high-speed engine which is 30
° The release immediately before isolation is also effective, 60 ° to 90% after dead center
By using heat energy concentrated around the first half of the best opportunity (hereinafter 60 ° to 90 ° after dead center is called the first half of the best opportunity),
As a result, the thermal efficiency and specific output at the same compression ratio are dramatically increased, and the compression ratio can be greatly increased, so that the normal entire combustion period (40 ° to 60 °) can be performed by the isolated combustion in the reduced-diameter main combustion chamber. As the de-isolation combustion, the approximate constant volume combustion is maintained for a long time under the best combustion conditions of high temperature and high pressure, and the constant volume combustion is approached (hereinafter referred to as approximate constant volume combustion) to complete the short period of complete combustion. At the same time, ultra-high-speed agitation mixed combustion based on the maximum pressure difference at the time of release of isolation further completes the combustion for a short period of time, thereby eliminating the possibility of discharging unburned components.
The main object of the present invention is to provide an apparatus and a method for an energy conservation cycle that can concentrate on a large reduction of x and aim at a great reduction of pollution.

Another object of the present invention is that it has been proved that the kinetic energy does not decrease at the time of collision in a completely elastic collision, and the pendulum movement of the watch has a very small loss of kinetic energy. The object is to provide an apparatus and a method in which the exercise is an energy conservation cycle with the least loss of kinetic energy. Another object of the present invention is to provide a high-pressure medium-temperature length in which the normal whole combustion period is energy-converted into a combustion period under the best combustion conditions of the maximum combustion pressure and the maximum combustion temperature and / or a superheated steam mass to which water injection is appropriately added. All fuels such as petroleum, propane, hydrogen, natural gas, methanol, etc. can be cycled, fuel-ignited, and scavenged by super-high-speed injection and agitation combustion of combustion gas due to time-separated combustion and / or a large pressure difference at the time of separation release. Regardless of the present invention, an apparatus and a method for achieving an energy conservation cycle in which complete combustion at medium temperature is completed and NOx and unburned components are almost completely eliminated at the same time. Another object of the present invention is to greatly reduce the loss of kinetic energy and greatly increase most of the heat energy near the dead center by storing and saving, so that the thermal efficiency is around 70% by concentrated use around the first half of the perfect aircraft. And an energy conservation cycle including a complete reciprocating engine. It is another object of the present invention to provide an apparatus and a method for energy saving cycles of small vibration, small size, light weight, and large output and ultra-large, lightweight, large output. Another object of the present invention is to provide an apparatus and a method for an energy conservation cycle of lean combustion in a reduced diameter main combustion chamber, stoichiometric air-fuel ratio combustion, excess fuel combustion, and increased specific output combustion (combustion that can be performed by a super short stroke engine). It is to be.

[0006]

SUMMARY OF THE INVENTION In view of the above-mentioned problems, the present invention provides a conventional non-constant-volume combustion (FIG. 1D) in which the volume of the combustion chamber rapidly increases and the temperature decreases as the piston descends.
The isolated combustion in the reduced-diameter main combustion chamber whose diameter has been reduced to one-fifth by limiting the
A, FIG. 2A, and FIG. 3A), an energy conservation cycle described later is performed, and a normal full combustion period (40 ° to 60 ° C.) is performed as an approximate constant volume combustion that is very close to the constant volume combustion of by-products.
°) is the maximum combustion pressure, the combustion under the best combustion conditions of the maximum combustion temperature, and / or the super-high-speed combustion gas injection agitation mixed combustion at the time of isolation release by the maximum pressure difference more than that. As the amount of heat energy (stroke volume of the reduced diameter piston) corresponding to the approximate constant volume combustion is increased, for example, the volume is increased by a factor of 25 with the volume increase of the prior art being 1 while keeping the remaining elements close to zero. In approximate constant volume combustion, the amount of heat energy used is 1/25 and 2/25
4- The thermal energy of the leakage amount is stored and stored in the reduced-diameter main combustion chamber and greatly increased (large pressure increase) (FIG. 1A) due to the law of conservation of mechanical energy and the approximate constant volume combustion, so that the mass of fuel combustion increases. It is possible to reduce the heat energy, and when the isolation is released (FIG. 1B), the heat energy of 24/25, which is greatly increased, is used for concentrated high-speed injection before and after the first half of the ideal machine. Mixed combustion provides the best combustion conditions for combustion and / or super-high torque due to the maximum bearing load on the perfect machine and / or large rotational power pollution including excessive fuel combustion in the reduced diameter main combustion chamber and stoichiometric air-fuel ratio combustion and lean combustion An energy saving cycle and method that enables a large reduction in combustion and / or thermal efficiency and a large increase in lightweight and large specific output simultaneously.

[0007] In addition, NOx reduction combustion is performed by isolated combustion in the reduced diameter main combustion chamber containing a large amount of residual gas. However, when the combustion chamber becomes gradually larger, the combustion temperature also gradually rises and NOx increase combustion occurs. The device is added to convert the high-temperature combustion gas temperature into the low-temperature superheated steam mass volume to convert the large-diameter combustion chamber into a low-temperature and low-pressure combustion chamber and a waste volume, and / or the lean combustion and the lean main combustion chamber. As stoichiometric air-fuel ratio combustion and excessive fuel combustion, and / or as a large-diameter combustion chamber that can greatly reduce the diameter and weight by greatly reducing vibration elements near the dead center, and / or adiabatic and non-cooling with a large-temperature, low-pressure large-diameter combustion chamber An apparatus and method for enabling an engine and / or enabling an ultra short stroke engine with a very wide choice of energy conservation cycles. That is, when the conventional technology is used as an energy storage cycle, almost all concerns are solved, and even if the compression ratio is the same, there is an effect of greatly increasing the compression ratio while greatly reducing the mechanical loss. It is anticipated that spark ignition engines will exceed this, but in order to obtain a complete reciprocating engine with a thermal efficiency of around 70%, it is necessary to further reduce the loss of kinetic energy by around 10% and make it almost zero. In other words, it has been proven that the kinetic energy does not decrease in the case of a perfect elastic collision, and the reciprocating motion of the pendulum of the watch is also used as a reciprocating motion with very little loss of kinetic energy. Therefore, the reciprocating motion of the piston is approximated to a completely elastic collision, and the crank mechanism is also replaced by a pendulum motion crank mechanism, whereby the kinetic energy reduction loss is reduced by about 10% by the pendulum piston, thereby making the pendulum piston an energy conservation cycle. It is planned to include a complete reciprocating engine with a thermal efficiency of around 70% depending on the method and method.

The crank mechanism has a dead center or 30 ° after the dead center.
There is a part where the power conversion efficiency is very poor (FIG. 1D), and in the prior art, this part consumes substantially all of the maximum (greater than the compression pressure) heat energy, so that most of the heat energy is increased in friction loss and the like. The thermal machine consumes almost no heat energy, the rotational force is greatly reduced, and the volume of the combustion chamber increases sharply with the lowering of the piston, so the combustion temperature drops sharply and suddenly shifts to the worst combustion conditions. Since the combustion becomes extremely non-constant-volume and the exhaust gas pollution greatly increases and the thermal efficiency greatly decreases, the present invention reduces the amount of heat energy used near the dead center (piston stroke volume) by using fuel as a necessary minimum. The savings and savings (Fig. 1A) greatly increase the power conversion efficiency, and the concentrated use around the first half of the ideal machine brings the maximum bearing load close to that of the ideal machine to achieve a large rotational force and / or thermal efficiency and light weight ratio Output at the same time Large increases and NO in to and / approximate constant volume combustion and the isolation releases during combustion close the possibility of residual unburned nil and / combustion process residual gas by improving the
x, and / or the addition of water injection in the reduced diameter main combustion chamber through near constant volume combustion to enable an adiabatic non-cooled engine / cycle number, fuel ignition system, fuel type,
Regardless of the scavenging method, the effect (Fig. 1B) is greater than that of greatly reducing the combustion ratio by greatly reducing the energy loss and mechanical loss and greatly increasing the compression ratio. That is, by providing the one-way air flow path, the isolated combustion in the reduced-diameter main combustion chamber which is reduced to, for example, 1/5 limited to the vicinity of the dead center can be performed by about 2/25.
The heat energy of 4 greatly increases due to the savings in the reduced-diameter main combustion chamber, and most of the heat energy is almost equal to the maximum pressure difference. In the conventional technology, the concentrated energy is used including the first half of the ideal machine (FIG. 1C) in which heat energy hardly remains in the prior art, so that a large rotating force greater than the compression ratio is greatly increased to generate carbon dioxide. To greatly reduce the amount of waste.

As described above, since the improvements are concentrated on the portion near the dead center where the power conversion efficiency is extremely poor, the solution is almost similar and the description is delicate and diverse. That is,
Vibration is increased mainly because the bearing load is not converted to rotational power even in the vicinity of the dead center even if the bearing load suddenly increases./In order to achieve ultra-large, lightweight, large output and small, lightweight, large output, the high-pressure combustion chamber is reduced to a small-diameter, low-pressure combustion chamber. The diameter should preferably be large and / or the reduced-diameter main combustion chamber is preferred for simultaneously obtaining excess fuel combustion and stoichiometric air-fuel ratio combustion and lean combustion, and / or the maximum bearing load must be at the dead center to increase the thermal efficiency. It is better to move from the vicinity to the first half of the aircraft, and / or the pollution reduction combustion requires two-stage combustion of near constant volume combustion and combustion at the time of release from isolation, and / or reduces vibration to simplify the structure. The large diameter reduces the number of cylinders. Therefore, in any case, the maximum bearing load due to an increase in the maximum combustion pressure is limited to the vicinity of the dead center, for example, as isolated combustion in the reduced diameter main combustion chamber reduced in size to 1/5.
Vibration is greatly reduced by a large reduction to one-third, etc., and ultra-large, lightweight, large-output, etc. are enabled as a significantly thinned reduced-diameter main combustion chamber and expanded-diameter combustion chamber. Most of the thermal energy greatly increased due to the pressure difference is intensively injected, and the maximum bearing load is moved to the first half of the ideal machine, greatly increasing the thermal efficiency. We will try to reduce it.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings based on embodiments, and portions having substantially the same structures as those of the embodiments will be denoted by the same names or symbols. The overlapping description will be omitted, and the characteristic portions and the portions that are insufficiently described will be sequentially described. In addition, the invention will be described in numerical form to specifically and clearly explain the intended purpose and anticipation, but is not limited to numerical figures. Referring to FIGS. 3 and 4, a first embodiment of an apparatus and a method for reducing vibration and using a pendulum piston crank engine as an energy conservation cycle will be described. All are fueled by ultra-high-speed injection-stirred mixed combustion (combustion on de-isolation) with the addition of water injection as the best combustion conditions at high temperature and pressure (approx. Constant volume combustion) and / or with a greater pressure difference. Regardless of the type of fuel, fuel ignition method, cycle number and scavenging method, the isolated combustion in the reduced-diameter main combustion chamber is used to complete the complete combustion of all fuels rapidly. It is almost nothing. Therefore, reduction of the combustion temperature is the biggest problem, and the combustion temperature is reduced by increasing the residual gas and adding an energy conversion means (water injection device) in a large combustion chamber, so that NOx and unburned components are simultaneously reduced to almost zero. Adiabatic uncooled engines are also possible. It is preferable that the opposed reciprocating motion of the double-ended piston is synchronized by the meshing synchronizing means 1 and the mechanical supercharger 2 to further reduce the vibration so as to challenge the outer diameter of the double-ended piston to 5 m or more, preferably two cycles. It is more preferable to make a completely elastic collision that explodes alternately on the left and right. Further, the normal piston rod is replaced with a pendulum arm, and the pendulum piston crank mechanism makes the pendulum motion of the watch very close to reduce the loss of kinetic energy by 10%. % Is more preferable.

In FIGS. 3 and 4, two double-headed enlarged pistons which reciprocate between inner dead center 3.3 and outer dead center 3.3 in cylinders provided opposite each other (FIG. Point positions), and the heads on both sides are appropriately recessed.
Is a dish-shaped recess), and when the isolation is released, ultra-high-speed injection is performed from the reduced-diameter main combustion chamber at substantially the maximum pressure difference. In order to reduce the thermal load, the isolated combustion period is selected according to the length of the reduced-diameter main combustion chamber, and the reduced-diameter piston that allows the amount of leakage to be selected is provided with an appropriate concave portion.
・ Protruding from the approximate center of 4 and providing in multiple stages annular irregularities 5 perpendicular to the direction of movement of the double-headed piston on the outer peripheral surface, making the convex portion at the front end wider and leaving the rear end appropriately A noise reduction groove 11 that extends obliquely in the direction of motion,
In addition to establishing the injection direction of the injected combustion gas and reducing noise, the pendulum holes 6.6 for inserting a pendulum arm and the piston cams 7.7 are provided substantially at the center of the cylindrical portion of the double-ended piston.
The pendulum arm swings up and down and right and left by the reciprocating motion of the double-headed enlarged piston, and the swing of the pendulum arm causes the piston cams 7 and 7 to rotate freely. As shown in FIG. 4, high-pressure combustion gas is injected and cooling loss is greatly reduced,
A reduced-diameter piston and an appropriate concave portion 4 are formed of a heat-resistant and corrosion-resistant material 9 and a heat-insulating material 10, and a cylinder head is provided in each cylinder, and the enlarged-diameter combustion chamber side is formed to have substantially the same shape as the appropriate concave portion 4. Is provided with a reduced-diameter main combustion chamber whose diameter is reduced to, for example, one-fifth of the expanded-diameter combustion chamber. And heat insulating material 10
To form a heat-resistant, corrosion-resistant and heat-insulating structure.

The central reduced-diameter main combustion chamber is made simpler and smaller and lighter by communicating with each other. When the compression ignition method is used as the fuel ignition system, each of the reduced-diameter main combustion chambers is adapted to the type of fuel. When the fuel injection device 18 is appropriately provided to add a glow hot surface or the like not shown in the drawing as usual and the spark ignition system is used, each of the reduced diameter main combustion chambers is appropriately provided in accordance with the type of fuel. Is provided with a fuel injection device 18 and an ignition plug (not shown), and when the diameter-reduced main combustion chamber is gradually increased, the combustion fuel mass and combustion time during the same combustion period (same crank angle) are gradually increased, and high-temperature combustion is performed. Therefore, it becomes increasingly difficult to reduce NOx by increasing the residual gas and shortening the isolated combustion period. Therefore, the water injection device 19 of the energy conversion means for injecting high pressure and high temperature water into the reduced diameter main combustion chamber is appropriately adjusted. Add and heat that water As that means, further 7-10
At least one of the exhaust heat exchange means 41, the reduced diameter heat exchange means 42, and the combustion heat exchange means 43 can be selected to greatly suppress the generation of NOx / The adiabatic non-cooled engine is made possible as a low-temperature, low-pressure combustion chamber, and the possibility of unburned fuel remaining due to near constant-volume combustion and combustion at the time of de-isolation is eliminated to greatly reduce pollution. For example, a reduced-diameter piston whose diameter is reduced to one-fifth of a double-headed expanded piston has a stroke volume reduced to one-fifth, so that the amount of heat energy used is reduced to one-fifth.
When there is no leakage, 24/25 thermal energy is stored and stored in the reduced-diameter main combustion chamber and greatly increased, so that the thermal energy greatly increases while saving fuel greatly (FIG. 1A).
Enables an adiabatic uncooled engine with water injection, and moves the maximum bearing load to the first half of the perfect aircraft by releasing isolated combustion (Fig. 1
B) to generate a large rotational force, to enable a great reduction of pollution by approximation constant volume combustion and combustion at the time of isolation release, and to perform super high speed injection mixing combustion of combustion gas having substantially the maximum pressure difference by the two-stage combustion (Fig. 1B) to make it almost impossible for unburned fuel to remain.

That is, in the prior art, as shown in FIG. 1D, near the dead point where the power conversion efficiency is the worst (dead point to 30 ° after the dead point), almost all of the maximum (not less than the compression pressure) heat energy is consumed (consumption amount). ), Most of the heat energy is consumed due to an increase in friction loss, etc., and the heat energy is reduced to a perfect opportunity, resulting in a large decrease in thermal efficiency. It is preferable that the isolated combustion in the main combustion chamber is normal, and the exception is that the small-sized high-speed engine can be released from the isolated combustion before 30 °, and the amount of heat energy used near the dead center is minimized. Therefore, the isolated combustion period is selected by adjusting the projecting length of the reduced diameter piston, but when the isolation is released, the complete combustion complete gas is mainly injected and agitated combustion at the substantially maximum pressure difference, or the unburned gas is super-high-speed injected and agitated combustion. Complete combustion is completed, but the limit of the stoichiometric air-fuel ratio combustion or excessive fuel combustion or mainly lean combustion can be achieved in the reduced diameter main combustion chamber, and the combustion maximum bearing load other than the compression pressure is limited to near the dead center. For example, it greatly reduces the vibration energy by moving the maximum bearing load to the first half of the ideal machine by greatly reducing it to 1/25 of that of the conventional technology. Requires means to complete combustion. Therefore, as shown in FIG. 4, on the outer peripheral surface of the diameter-reducing piston, a number of annular irregularities 5 perpendicular to the direction of movement of the double-headed diameter-expanding piston are provided, the projection at the tip is widened, and the base part is appropriately left. On its outer peripheral surface, a plurality of noise reduction grooves 11 extending obliquely with respect to the direction of movement of the double-headed enlarged piston are provided to reduce noise and establish a jet of high-speed injection gas to promote agitated mixed combustion, Efficient injection to double-headed pistons to increase torque. The essential configuration for the energy conservation cycle as isolated combustion in the reduced diameter main combustion chamber is a reed valve that allows communication only between the reduced diameter main combustion chamber and the expanded diameter combustion chamber to allow only flow toward the reduced diameter main combustion chamber. A one-way air flow path 21 provided with a suitable check valve 20 including at least one
It is to establish more than a pair. The one-way air flow path 21 minimizes the increase in compression power and allows the compression ratio to be increased.
As the isolated combustion in the reduced diameter main combustion chamber, the two-stage combustion of approximately constant volume combustion and combustion at the time of release of isolation greatly reduces pollution and friction loss. (Heat energy greatly increased)
Then, the maximum bearing load is moved to the first half of the ideal machine (Fig. 1B), and most of the heat energy is converted to large rotational power, thereby greatly increasing the thermal efficiency and greatly reducing pollution.

As shown in FIG. 3, FIG. 4, and FIG. The reciprocating motion of the piston causes the pendulum arm to perform a pendulum motion, and to rotate the crankshaft 25 pivotally supported at the lower ends of the husband and wife to obtain power,
An exhaust outlet 23 for exhausting from the expanded combustion chamber through each of the cylinder holes 22 is appropriately provided for each of them, and a scavenging inlet 24 for scavenging the expanded combustion chamber for each is appropriately provided for each. To form a large-diameter combustion chamber that is, for example, five times larger than the diameter-reduced main combustion chamber. That is, since the water-injection device 19 can be added to the expanded combustion chamber by isolated combustion in the reduced-diameter main combustion chamber, the maximum bearing load in the vicinity of the dead center is reduced to 1/25, etc. Because of the low pressure, large diameter expansion, adiabatic non-cooling, and significantly thinner, lighter weight and larger output are possible compared to the conventional technology.
The pendulum arm that makes a pendulum motion by the opposed reciprocating motion of the double-headed enlarged piston easily reciprocates up and down, and pivots the crankshafts 25 at the lower end of the pendulum arm. The upper end of the pendulum arm is rotatably supported while moving along the semicircular track 8.8, while being inserted between the piston-side cams 7.7 rotatably supported while moving 8.8. Are inserted between the main body side cams 26, 26, and the pendulum arms of each husband swing right and left and up and down by opposing reciprocating motion of the double-headed enlarged pistons, thereby rotating the crankshafts 25 and 25 to generate power. Convey The meshing synchronizing means 1 and the mechanical supercharger 2 for synchronizing the opposing reciprocating motions of the double-ended pistons are appropriately configured including the mechanical supercharger 31 and the synchronizing means 32 described in the earlier application, and Shaft 25
7 to 10, the air outlet 27 communicates with the scavenging inlet 24, and the air inlet 28 communicates with the air inlet 28 through the outlet of a conventional turbocharger 29,
The turbocharger 29 is connected to the exhaust outlet 23 and operated by exhaust gas as usual. When the mechanical supercharger 2 is not used, the turbocharger directly scavenges the enlarged combustion chamber by the scavenging inlet 24.
More scavenging.

When the output is small or when the configuration is as simple as possible, the second embodiment shown in FIG. 2 may be used. In other words, in the isolated combustion of the super-large reduced-diameter main combustion chamber, the opposed pistons are synchronized to reduce the vibration to the limit and to maximize the limit of the high output and the low vibration. The thermal energy that is converted to vibration near the dead center is as small as 1/25 of the prior art so as to reduce the maximum bearing load etc. to, for example, 1/25. In order to release the isolated combustion when approaching the first half of the perfect aircraft, the conventional technology converts vibration energy into rotational power to produce large rotational force. Therefore, FIG.
It is anticipated that the second embodiment of the present invention can be put to practical use because vibration can be greatly reduced and a large rotating force can be obtained. In addition, since the double-ended diameter piston is one in the first embodiment, a four-cycle engine can be provided by providing a valve operating mechanism and an intake valve not shown. FIG. 2 shows a two-cycle uniflow scavenging pendulum piston energy conservation cycle engine with reduced kinetic energy, reduced loss (as fully elastic impact and pendulum motion), increased specific power and reduced thermal load on the cylinder, and therefore exhaust. Outlet 23 is replaced with exhaust valve 30 and scavenging inlet 24. Another difference is that the single crankshaft 25 in FIG. 5 eliminates the need for the meshing synchronizing means 1 and as an optional mechanical supercharger 2 and / or a turbocharger 2
9, and / or the two-cycle engine using any one of the superchargers.

FIGS. 5 to 10 show Japanese Patent Application No. 8-17275.
5 (fifth priority claim application) Figures 5 to 10 are directly quoted. For example, in FIG. 3, the meshing synchronizing means 1 and the mechanical supercharger 2 for synchronizing the opposing reciprocating motions of the respective double-headed enlarged pistons rotate the respective crankshafts 25 by meshing the two gears (meshing). Including the blower), as shown in FIG.
And the air is sent from the air inlet 28 to the air outlet 27 as usual (see FIGS. 7 to 10), but the meshing synchronization means 1 and the mechanical supercharger 2 are not used as the mechanical supercharger 2. In this case, use it as the meshing synchronization means 1. As shown in Fig. 2, when the meshing synchronization means 1 is unnecessary, use a flywheel not shown in the figure as usual. In the prior art, one cylinder (one combustion chamber) is connected to the crankshaft 25. However, in the pendulum piston crank mechanism, two cylinders (two expanded combustion chambers) are connected. In FIG. 2 with one shaft, two cylinders, four cylinders, six cylinders and two cylinders
In FIG. 3 with two crankshafts, four cylinders are used for each cylinder.
A multi-cylinder engine will be used in units of cylinders, eight cylinders, twelve cylinders and four cylinders. The check valve 20 shown in FIG. 6 is used to form a one-way air flow path 21 which connects the reduced-diameter main combustion chamber and the expanded-diameter combustion chamber and allows only a flow toward the reduced-diameter main combustion chamber. The configuration of the check valve 20 including the reed valve is not limited as long as the one-way air flow path 21 can be formed in the head. However, when the check valve 20 is inserted and fixed from the expanded combustion chamber side, the heat load of the check valve 20 is reduced. Since the dead volume of the reduced-diameter main combustion chamber can be increased, it is preferable to use an ultra-lean combustion two-cycle engine as a mainstream. Therefore, the check valve 20 shown in FIG.
While being pressed and urged by 8, the one-way air flow path 21 is inserted and fixed from the side of the expanded diameter combustion chamber to form the one-way air flow path 21. In addition, the oblique air flow path 39 for generating turbulence by the air flow injected from the one-way air flow path 21 to promote the combustion of the injected fuel is provided in the vicinity of the heat-resistant and corrosion-resistant material 9 or its part which is not closed by the reduced-diameter piston. It is preferred to provide.

When the isolated combustion is performed in the reduced-diameter main combustion chamber, the piston cycle is subjected to two-stage combustion of approximately constant-volume combustion and combustion at the time of release of the isolation. An energy conservation cycle is possible, but even with the limit of lean combustion when using near constant volume combustion, the maximum combustion pressure in large combustion chambers rises significantly due to storage savings, increasing residual gas to the limit and increasing the isolated combustion period. Even if it is shortened to the limit, NOx increase combustion will occur, so an energy conservation cycle in which a water injection device 19 is added to the reduced-diameter main combustion chamber enables various medium-temperature isolated combustion.
Referring to FIGS. 7 to 10, various types of intermediate-temperature isolation combustion will be described. In the apparatus and method of the A-type energy storage cycle shown in FIG. Dedicated to reducing NOx by saving (ultra-lean combustion in the reduced diameter main combustion chamber) and increasing residual gas, greatly reducing pollution, and further eliminating unburned parts by burning when the reduced diameter main combustion chamber is released. Injecting into the head of the expanding piston as speed type dynamic pressure large thermal energy + static pressure thermal energy, converting it into large rotating power in the expanding combustion chamber, generating a large output and discharging from the exhaust outlet 23, The turbocharger 29
Is operated to pressurize the intake air and exhaust air from the exhaust section. The pressurized air may be directly scavenged in the expanded combustion chamber from the air outlet 27, and further pressurized by mechanical supercharging through the air inlet 28, and the scavenging inlet 24 of the expanded combustion chamber is increased.
The super-high-charge can be selected at the same time, and it shifts to the isolated combustion in the reduced-diameter main combustion chamber using the one-way air flow path 21 and the reduced-diameter piston.

In the apparatus having the B-type energy storage cycle shown in FIG. 8, when the size of the combustion chamber gradually increases, the combustion shifts to NOx increase combustion. Energy conversion of gas temperature to low temperature superheated steam mass volume, and even if the maximum combustion pressure rises significantly due to storage savings, energy conversion means (water injection device) is added to the lean combustion and increase of residual gas, NOx generation is almost eliminated by isolated combustion at the middle temperature and high compression diameter main combustion chamber. Therefore, as shown in FIG. 4, the water injection device 19 is appropriately added and / or the fuel injection device 18 is added.
And the water injection device 19 are appropriately combined, and the high-pressure high-temperature water heated by an arbitrary exhaust heat exchange device 41 is injected from the respective water injection devices 19 controlled by the control device 40. With the addition, the maximum combustion pressure can be significantly increased to achieve a medium-temperature, high-pressure isolation combustion, and NOx generation is almost eliminated. In the apparatus having the C-type energy storage cycle shown in FIG. 9, a large-diameter high-pressure high-temperature water further heated to a high temperature is added to the control apparatus 40 by adding a reduced-diameter heat exchange means 42 to the B-type energy storage cycle. Injection from the water injection device 19 increases the amount of energy conversion to reduce the stoichiometric air-fuel ratio in the diameter-reduced main combustion chamber and the excess and lean combustion, and to increase the maximum combustion pressure. It makes it possible to provide an adiabatic non-cooled engine while making the generation almost zero. The apparatus having the D-type energy storage cycle shown in FIG. 10 is capable of injecting a large amount of high-pressure high-temperature water heated to a higher temperature by adding the combustion part heat exchange means 43 to the C-type energy storage cycle. The amount can be greatly increased and injected from each of the water injection devices 19 controlled by the control device 40 to eliminate the generation of NOx as a medium-temperature high-pressure isolated combustion that can greatly increase the maximum combustion pressure.

[0019]

As described above, the present invention has many effects. Particularly, in the prior art, the maximum heat energy (not less than the compression pressure) is obtained in the dead center where power conversion efficiency is the worst or 30 ° after the dead center. Heat energy (Fig. 1D) is consumed (the amount used is reduced), so that the efficiency of conversion to rotational power is extremely low, and the thermal efficiency is greatly reduced due to a large increase in friction loss. However, by using an energy conservation cycle, the amount of heat energy used from the dead center to 30 ° after the dead center is greatly reduced, for example, by a factor of 25, thereby greatly reducing the mechanical loss and the fuel combustion mass. While saving heat, the heat energy is greatly increased (combustion pressure is greatly increased).
By releasing the isolated combustion in the reduced-diameter main combustion chamber while appropriately leaking heat energy such as 24 / 25th, a large effect greater than the compression ratio greatly increased by the conventional technology is generated by the energy storage cycle, and the large rotational force is obtained. In the prior art, since almost all of the maximum heat energy is consumed from the dead center to 30 ° after the dead center, the volume of the combustion chamber is rapidly expanded, and the worst case of low pressure and low temperature is achieved. It was extremely difficult to reduce pollution due to extreme non-constant volume combustion, in which combustion rapidly deteriorated due to rapid transition to combustion conditions. The two-stage combustion makes it possible to greatly increase the residual gas and / or enables the adiabatic non-cooled engine by appropriately adding energy conversion means and heat exchange means. type Fine ignition system and the number of cycles and regardless of the scavenging system, there is a large effect that the thermal efficiency large rises and at the same time nothing to bring the NOx and unburned.

[Brief description of the drawings]

FIG. 1 is a schematic graph for comparing a change in combustion chamber pressure with respect to a crank angle in an energy storage cycle according to the present invention with a conventional technique.

FIG. 2 is a partial cross-sectional view of a second embodiment illustrating reciprocating motion of the double-ended piston of the present invention as an energy conservation cycle and explaining complete elastic collision and pendulum motion.

FIG. 3 is a partial cross-sectional view of the first embodiment of the present invention in which vibration is reduced to the utmost and the pendulum piston has an energy conservation cycle.

FIG. 4 is a partial cross-sectional view illustrating an embodiment of a reduced-diameter main combustion chamber and a double-ended expanded piston according to the present invention.

FIG. 5 is a partial cross-sectional view illustrating the meshing synchronization means and the crankshaft according to the present invention.

FIG. 6 is a cross-sectional view of the check valve according to the embodiment of the present invention.

FIG. 7 is a schematic diagram of a method for making the present invention an A-type energy storage cycle.

FIG. 8 is a schematic diagram of a method for making the present invention a B-type energy storage cycle.

FIG. 9 is a schematic diagram of a method for making the present invention a C-type energy storage cycle.

FIG. 10 is a schematic diagram of a method for making the present invention a D-type energy storage cycle.

[Explanation of symbols]

1: meshing synchronization means 2: mechanical supercharger 3: dead center 4: concave portion 5: annular unevenness 6: pendulum hole
7: piston side cam 8: semi-circular track 9: heat and corrosion resistant material 10: heat insulating material 11: noise reduction groove 12:
Pendulum side cam 13: Parallel track 14: Convex portion 18: Fuel injection device 19: Water injection device 20: Check valve 21: One-way air flow path 22: Cylinder hole 23: Exhaust outlet 24: Scavenging inlet 2
5: Crankshaft 26: Body side cam 27: Air outlet 28: Air inlet 29: Turbocharger 3
0: exhaust valve 36: valve seat 37: valve body 38: valve spring 39: oblique air flow path 40: control device 41: exhaust section heat exchange means 42: reduced diameter section heat exchange means 43: combustion section heat exchange means

────────────────────────────────────────────────── ─── Continued on the front page (51) Int.Cl. ⁶ Identification code FI F02B 75/28 F02B 75/32 A 75/32 F02D 15/04 H F02D 15/04 F02F 3/00 E F02F 3/00 3 / 28 Z 3/28 F02B 37/00 301H

Claims (63)

[Claims] 1. A diameter-reduced piston whose diameter has been appropriately reduced is projected from substantially the center of the left and right enlarged pistons reciprocating between a left dead center and a right dead center in a cylinder. A head is provided to form a reduced-diameter main combustion chamber that accommodates the reduced-diameter piston and that is optimally reduced in diameter so that isolated combustion can be performed. In a device in which the piston reciprocates, makes the pendulum move to the pendulum arm, and rotates the crankshaft by the pendulum movement to obtain a rotational power, the inside of the double-head enlarged piston and the main body side have:
A piston-side cam and a body-side cam for inserting and maintaining the middle and one end of the pendulum arm, respectively, are provided on a semicircular orbit so as to face each other, and the middle and one end of the pendulum arm are inserted and maintained, respectively.
The crankshaft (25) rotatably supported by the lower end of the pendulum arm is rotated by the reciprocating motion of the double-headed enlarged piston to enable transmission of power, allowing the reduced-diameter main combustion chamber to communicate with the increased-diameter combustion chamber,
A device having an energy conservation cycle having at least one or more sets of one-way air flow paths each provided with a check valve (20) allowing only a flow toward the reduced diameter main combustion chamber. 2. A reduced-diameter piston whose diameter is appropriately reduced from a substantially right and left center of each of two double-headed enlarged pistons reciprocating between an outer dead center and an inner dead center in a cylinder provided opposite to each other. A cylinder head is provided in each of the cylinders provided so as to be opposed to each other to form a reduced-diameter main combustion chamber which accommodates the reduced-diameter piston and is optimally reduced in diameter so as to be capable of isolated combustion. The double-headed enlarged pistons reciprocate in opposite directions by the isolated combustion and release of the husband in the reduced diameter main combustion chamber, causing the respective pendulum arms to perform a pendulum motion, and rotating the respective crankshafts (25) by the pendulum motion. In the energy storage cycle, the piston-side cam (7) and the body-side cam (7) for inserting and maintaining the middle and one end of the pendulum arm, respectively, inside and on the body side of the double-headed piston. 26)
Are placed on the semicircular orbit of the husband and wife, and the middle and one end of the husband and wife's pendulum arms are inserted and maintained, and the opposite reciprocating motion of the double-headed piston expands the lower end of the husband's pendulum arm. A rotatably supported crankshaft (25) rotates to transmit power, communicates with the reduced-diameter main combustion chamber and the expanded-diameter combustion chamber, and controls only the flow toward the reduced-diameter main combustion chamber. Apparatus for an energy conservation cycle having at least one or more sets of one-way air passages (21) provided with a check valve (20) enabling the same. 3. The energy according to claim 1, wherein the reduced-diameter piston is provided with annular irregularities perpendicular to the direction of movement of the double-head enlarged piston on an outer peripheral surface thereof. A device with a storage cycle. 4. The diameter-reducing piston is provided with a large number of annular irregularities on the outer peripheral surface thereof orthogonal to the direction of movement of the double-headed diameter-expanding piston. 3. The energy saving cycle device according to claim 1, further comprising a plurality of noise reduction grooves (11) extending obliquely to the direction of movement of the double-ended piston, while appropriately leaving a lower portion. 5. A fuel injection device (18) for injecting fuel into the reduced diameter main combustion chamber, wherein the injected fuel and air flowing through the one-way air flow path are connected to the reduced diameter main combustion chamber. 5. The device according to claim 1, wherein the turbulence is formed in the combustion chamber. 6. The reduced-diameter piston is inserted and maintained in the reduced-diameter main combustion chamber to form an isolation period of the isolated combustion in the reduced-diameter main combustion chamber over a predetermined period after a dead center.
An energy storage cycle device according to any one of claims 5 to 5. 7. A water injection device (19) for injecting water into the reduced-diameter main combustion chamber, wherein each of the heat exchange means (41), (42), and (43) heats the water. At least one
Apparatus as claimed in any one of claims 1 to 6 comprising means or more. 8. A one-way air flow path provided with the check valve (20) is provided at least one set, and the check valve is inserted and fixed from the expanded combustion chamber side. An apparatus having an energy conservation cycle according to any one of the preceding claims. 9. The heat-resistant, corrosion-resistant, heat-insulating structure made of a heat-resistant, corrosion-resistant material and a heat-insulating material for a head of the reduced-diameter main combustion chamber, the reduced-diameter piston, and the double-ended double-diameter piston. An apparatus having the energy storage cycle according to claim 1. 10. A heat-resistant and corrosion-resistant material (9) for said reduced-diameter main combustion chamber.
10. The apparatus according to claim 1, further comprising an oblique air passage (39) of a one-way air passage (21). 11. The double-headed enlarged-diameter piston having a reduced-diameter piston protruding portion formed as a dish-shaped recess (4).
0. An apparatus having an energy storage cycle according to any one of 0. 12. The cylinder head according to claim 1, wherein the reduced-diameter piston projecting portion of the double-ended piston is an appropriate concave portion, and the corresponding cylinder head is an appropriate convex portion. Energy conservation cycle device. 13. The energy storage cycle according to claim 1, wherein the reduced-diameter piston projecting portion of the double-ended piston is a flat portion, and the corresponding cylinder head is a flat portion. apparatus. 14. A heat-resistant and corrosion-resistant material (9) for the reduced-diameter main combustion chamber.
14. The device according to claim 1, further comprising a spark plug for spark ignition penetrating the heat insulating material (10). 15. A heat and corrosion resistant material (9) for said reduced diameter main combustion chamber.
14. An apparatus according to any one of the preceding claims, wherein a compression glow is provided by providing a glow hot surface through the heat insulator (10). 16. A heat-resistant and corrosion-resistant material (9) for said reduced-diameter main combustion chamber.
16. The device according to any one of claims 1 to 15, wherein the fuel is injected by providing a fuel injection device (18) through the heat insulating material (10). 17. The fuel injection device according to claim 1, wherein the fuel injection device is provided in the reduced-diameter main combustion chamber so as to face the direction of movement of the double-headed piston and inject fuel. Energy conservation cycle device. 18. The water injection device according to claim 1, wherein the water injection device (19) is provided in the reduced diameter main combustion chamber so as to face the movement direction of the double-headed enlarged piston to inject water. An apparatus having an energy conservation cycle as described. 19. A piston-side cam (7) for inserting and maintaining an intermediate portion of a pendulum arm inside the double-head enlarged piston.
Are provided opposite to the semicircular track (8) to insert and maintain the pendulum arm, and a main body side cam (26) for inserting and maintaining one end of the pendulum arm is also provided at the upper part of the main body to oppose the pendulum arm. The crankshaft (25) rotatably supported at the lower end of the splittable pendulum arm while inserting and maintaining the arm is rotatable by a reciprocating motion of the double-headed piston to transmit power. Apparatus with an energy conservation cycle according to any one of claims 18 to 19. 20. A piston-side parallel track (13) for inserting and maintaining a pendulum-side cam (12) at an intermediate portion of a pendulum arm is provided inside the double-headed enlarged piston, and the pendulum-side cam is inserted. A main body side cam (26) for maintaining and inserting one end of the pendulum arm also at the upper part of the main body side is provided opposite to the semicircular track (8) so that the pendulum arm is inserted and maintained. 19. The energy storage cycle apparatus according to claim 1, wherein a crankshaft rotatably supported at a lower end is rotated by a reciprocating motion of a double-headed piston to transmit power. 21. An interlocking synchronizing means (1) for synchronizing the opposed reciprocating motion of the double-headed enlarged piston is provided at the end of each crankshaft (25) to synchronize the opposed reciprocating motion of the double-headed enlarged piston. An apparatus as an energy storage cycle according to any one of claims 2 to 20. 22. A double-head widening piston (25) is provided at the end of each crankshaft (25) with an interlocking synchronizing means (1) and a mechanical supercharger (2) for synchronizing opposing reciprocating movements of the double-head widening piston. 21. The apparatus according to any one of claims 2 to 20, wherein the opposed reciprocating motion of the radial piston is synchronized. 23. The energy storage cycle apparatus according to claim 1, further comprising a mechanical supercharger provided at an end of the crankshaft. 24. A multi-cylinder engine in which the number of cylinders including an expanded combustion chamber is increased in increments of two cylinders to two, four, and six cylinders in order to rotate the crankshaft (25).
An energy storage cycle apparatus according to any one of claims 23 to 23. 25. A multi-cylinder engine in which the number of cylinders including the expanded combustion chamber is increased to four, eight and twelve cylinders in four-cylinder increments in order to rotate the crankshaft (25). An energy storage cycle apparatus according to any one of claims 23 to 23. 26. The fuel cell system according to claim 1, wherein the isolated combustion in the reduced-diameter main combustion chamber, which is appropriately reduced in diameter, is defined as excessive fuel combustion.
An energy storage cycle according to any one of claims 5 to 10. 27. The isolated combustion in the reduced-diameter main combustion chamber appropriately reduced in diameter is a fuel-lean combustion.
An energy storage cycle according to any one of claims 5 to 10. 28. The apparatus according to claim 1, wherein the fuel is mainly gasoline. 29. The apparatus according to claim 1, wherein the fuel is mainly light oil. 30. The apparatus according to claim 1, wherein the fuel is mainly heavy oil. 31. An apparatus according to any one of claims 1 to 27, wherein the fuel is mainly propane. 32. The apparatus according to any one of claims 1 to 27, wherein the fuel is mainly hydrogen. 33. The apparatus according to claim 1, wherein the fuel is mainly natural gas. 34. The apparatus according to any one of claims 1 to 27, wherein the fuel is mainly methanol. 35. A reciprocating piston cycle comprising a compression step, a heating step, an expansion step, and an exhaust step, wherein in the heating step, the piston is appropriately contracted for a predetermined period after the left and right dead points of the double-headed piston. By performing isolated combustion in the reduced diameter main combustion chamber, the optimal amount of heat energy is stored until the isolated combustion is released, and injected into the double-headed enlarged piston as speed-type thermal energy, etc. A method in which a motion causes a crankshaft, which is pivotally supported at the lower end of a pendulum arm, to rotate to produce a large rotational force near the first half of an ideal machine, thereby providing an energy conservation cycle. 36. A reciprocating piston cycle comprising a compression step, a heating step, an expansion step, and an exhaust step, wherein in the heating step, after the inner dead center and the outer dead center of each of the opposed double-head enlarged pistons. By performing isolated combustion in the reduced-diameter main combustion chamber for a predetermined period thereafter, an optimal amount of thermal energy is stored until the isolated combustion is released, and injected into the double-headed piston as velocity-type thermal energy or the like. Then, each of the two head-expanding pistons reciprocates to rotate their respective crankshafts, which are pivotally supported at the lower ends of the pendulum arms, to generate an energy saving cycle in the vicinity of the first half of the ideal machine. 37. A non-return valve communicating with the reduced-diameter main combustion chamber and the expanded-diameter combustion chamber to allow only the flow toward the reduced-diameter main combustion chamber to perform isolated combustion in the reduced-diameter main combustion chamber. (20)
37. The method of claim 35 or claim 36, wherein at least one or more sets of one-way air passages (21) provided with are provided. 38. The timing for releasing the isolated combustion in the reduced-diameter main combustion chamber is set at 30 crank angles after the dead center of each piston.
38. The method according to any one of claims 35 to 37, wherein the velocity-type thermal energy is injected into the double-headed enlarged piston from about 0 ° to about 60 °. 39. The timing at which the isolated combustion in the reduced diameter main combustion chamber is released is set at 40 degrees of the crank angle after the dead center of each piston.
38. The method as claimed in any one of claims 35 to 37, wherein the velocity type thermal energy is injected into the double-ended piston with the angle between about 90 ° and about 70 °. 40. The energy according to any one of claims 35 to 39, wherein by performing isolated combustion in said reduced diameter main combustion chamber, approximate constant volume combustion is brought close to constant volume combustion. How to make a save cycle. 41. The method according to any one of claims 35 to 40, wherein the isolated combustion in the reduced diameter reduced main combustion chamber is an excess fuel combustion. 42. The method according to any one of claims 35 to 40, wherein the isolated combustion in the reduced diameter main combustion chamber is stoichiometric air-fuel ratio combustion. 43. The method according to claim 35, wherein the isolated combustion in the reduced diameter main combustion chamber is a lean burn. 44. The approximate constant-volume combustion is performed by isolating combustion in a reduced-diameter main combustion chamber containing a large amount of residual gas, so that NOx and unburned components are continuously maintained for a predetermined period after the dead center of each of them. 44. The method as set forth in any one of claims 35 to 43, wherein the energy storage cycle is almost zero at the same time. 45. An energy conversion means for injecting water into the reduced-diameter main combustion chamber to add the constant-constant combustion to medium-temperature and high-pressure combustion by isolating combustion in the reduced-diameter main combustion chamber containing a large amount of residual gas. NO for a predetermined period after the dead center
45. The method as set forth in any one of claims 35 to 44, wherein x and unburned components are simultaneously made almost zero. 46. The head of the double-ended piston receiving the injection of the velocity-type thermal energy is formed as a dish-shaped recess (4), and the corresponding cylinder head is formed as a dish-shaped projection (14). 46. A method according to any one of the preceding claims, wherein the energy conservation cycle is performed. 47. The method according to claim 35, wherein the head of the double-headed enlarged diameter piston receiving the injection of the velocity type thermal energy is a flat portion, and the corresponding cylinder head is also a flat portion. A method that uses an energy conservation cycle. 48. The head of the double-headed enlarged piston receiving the injection of the velocity-type thermal energy is an arbitrary concave part (4), and the corresponding cylinder head is an arbitrary convex part (14). 48. A method according to any one of claims 47 to 47, wherein the energy conservation cycle. 49. The reduced-diameter piston is projected from substantially the center of the head of the double-head enlarged piston in accordance with the reduced diameter of the reduced-diameter main combustion chamber, and has an outer peripheral surface in the movement direction of the double-head enlarged piston. 50. A leakage amount is selected by providing a large number of orthogonal annular irregularities to reduce the pressure of the high-pressure combustion gas in multiple stages.
A method as an energy conservation cycle according to any one of the preceding claims. 50. On the outer peripheral surface of the reduced-diameter piston, multi-stage annular irregularities perpendicular to the direction of movement of the double-headed enlarged piston are provided. 50. The energy storage cycle according to any one of claims 35 to 49, wherein a plurality of noise reduction grooves (11) extending obliquely to the direction of movement of the double-headed enlarged piston are provided while appropriately leaving a lower portion. And how. 51. The apparatus according to claim 35, wherein the isolated combustion in the reduced diameter main combustion chamber is canceled at an optimum time to increase the output in the vicinity of the first half of the ideal machine after the dead center of each husband and wife. Energy conservation cycle. 52. A one-way air flow path formed by inserting and fixing a check valve that allows only the flow toward the reduced-diameter main combustion chamber from the enlarged-diameter combustion chamber side. 51
A method as an energy conservation cycle according to any one of the preceding claims. 53. By reducing the diameter of the reduced-diameter main combustion chamber,
53. The energy storage device according to any one of claims 35 to 52, wherein the high-pressure reduced-diameter main combustion chamber has a small diameter, thin wall, and light weight, and the expanded diameter combustion chamber has a large diameter, thin wall, and light weight as a substantially low-pressure combustion chamber. How to make a cycle. 54. By reducing the diameter of the reduced-diameter main combustion chamber,
The vibration energy near the dead center of the husband and wife is greatly reduced.
54. A method as in any one of claims 53. 55. An energy conversion means for injecting water into the reduced-diameter main combustion chamber is added to the isolated combustion in the reduced-diameter main combustion chamber,
55. The method according to any one of claims 35 to 54, wherein the expanded combustion chamber is a low-temperature low-pressure combustion chamber to enable an adiabatic non-cooled engine. 56. The isolated combustion in the reduced-diameter main combustion chamber,
56. The method according to any one of claims 35 to 55, wherein the approximate constant volume combustion period under the best combustion conditions is greatly extended. 57. The isolated combustion in the reduced diameter main combustion chamber,
57. The energy storage cycle according to any one of claims 35 to 56, wherein the approximate constant-volume combustion period under the best combustion conditions is extended, and ultra-high-speed agitated mixed combustion is performed by a large pressure difference when the isolated combustion is released. And how. 58. The isolated combustion in the reduced-diameter main combustion chamber,
35. Claims 35 to 35, wherein the constant-combustion combustion and the ultra-high-speed agitated mixed combustion shorten the complete combustion termination period, thereby increasing the diameter of the double-headed piston and greatly increasing the specific output by the ultra-short stroke engine. 58. A method as in any one of paragraph 57 to the energy conservation cycle. 59. A piston-side cam (7) for inserting and maintaining an intermediate portion of a pendulum arm inside the double-headed enlarged piston.
The pendulum arm is inserted and maintained in opposition to the semicircular orbit (8), and the crankshaft (25) pivotally supported at the lower end of the pendulum arm is rotated by the reciprocating motion of the double-headed enlarged piston to transmit power. 59. A method as claimed in any one of claims 35 to 58, wherein the method comprises an energy conservation cycle. 60. A parallel orbit (13) for inserting and maintaining a pendulum-side cam (12) of a pendulum arm is provided in the inside of the double-headed enlarged piston so as to face the pendulum arm, and the pendulum arm is inserted and maintained.
60. The energy storage cycle according to any one of claims 35 to 59, wherein the reciprocating motion of the double-headed piston rotates the crankshaft (25) pivotally supported at the lower end of the pendulum arm to transmit power. And how. 61. Each of the crankshafts (25) is coupled to each other by a meshing synchronizing means (1) for synchronizing opposing reciprocating motions of the double-headed enlarged piston. Energy conservation cycle. 62. The crankshaft according to any one of claims 35 to 60, wherein each of the crankshafts is connected by a meshing synchronizing means and a mechanical supercharger for synchronizing the opposed reciprocating motions of the double-head enlarged piston. Energy conservation cycle. 63. The method according to claim 36, wherein a mechanical supercharger is provided on the crankshaft.